Exhaust heat collecting system

ABSTRACT

In one embodiment, an exhaust heat collecting system of collecting exhaust heat in a fluid treatment system. The fluid treatment system includes a fluid path to convey at least an operating fluid or a cooled fluid among first and second heat source fluids, the operating fluid and the cooled fluid. The fluid treatment system further includes a fluid treatment module including an expansion module, a power generator and a condenser for the operating fluid, or including a heat absorbing module and a heat releasing module for the cooled fluid. The exhaust heat collecting system includes a water path to heat water by using the condenser or the heat releasing module, and a heater to heat the water from the water path by using the first or second heat source fluid or the operating fluid to produce the water to be used as hot water or to produce steam.

CROSS REFERENCE TO RELATED APPLICATIONS

This application is based upon and claims the benefit of priority fromthe prior Japanese Patent Applications No. 2015-201282, filed on Oct. 9,2015, No. 2016-139375, filed on Jul. 14, 2016 and No. 2016-140406, filedon Jul. 15, 2016, the entire contents of which are incorporated hereinby reference.

FIELD

Embodiments described herein relate to an exhaust heat collectingsystem.

BACKGROUND

FIG. 37 is a schematic diagram showing a first example representing theconfiguration of a conventional power generating system.

The power generating system in FIG. 37 includes a heat source fluidheater 1, a heat source fluid pump 2, a heat source fluid path 3, anevaporator 4, an operating fluid pump 5, an operating fluid path 6, anexpansion module 7, a power generator 8, a condenser 9, a cooling waterpump 11, a cooling water path 12, a cooling tower 13, a blower 14 and anatmosphere introducing portion 15.

The heat source fluid is conveyed through the heat source fluid path 3by the heat source fluid pump 2, and is heated by the heat source fluidheater 1. An example of the heat source fluid heater 1 is a small-sizedbiomass boiler that burns biomass fuel of a wooden chip or the like, andan example of the heat source fluid is water of a gas or a liquid. Inthis case, the heat source fluid heater 1 heats the water of the liquidby combustion exhaust gases generated by burning the biomass fuel, thusconverting the water of the liquid into water (steam) of the gas.Another example of the heat source fluid heater 1 is a solar energycollector, and an example of the heat source fluid in this case isthermal medium oil. A further other example of the heat source fluidheater 1 is an exhaust heat collector that collects factory exhaust heator the like, and an example of the heat source fluid in this case iswater. The heat source fluid discharged from the heat source fluidheater 1 flows into the evaporator 4, and is lowered in temperature byheating the operating fluid in the evaporator 4. The heat source fluidcirculates between the heat source fluid heater 1 and the evaporator 4through the heat source fluid path 3.

The operating fluid of the liquid is conveyed through the operatingfluid path 6 by the operating fluid pump 5 and is heated by theevaporator 4 to be converted into the operating fluid of a gas. That is,the operating fluid evaporates. An example of the operating fluid is alow-boiling medium of chlorofluorocarbon (CFC) or the like. Theoperating fluid discharged from the evaporator 4 flows into theexpansion module 7 and expands in the expansion module 7 to drive arotational shaft of the expansion module 7. An example of the expansionmodule 7 is a turbine. The rotational shaft of the expansion module 7 isconnected to the power generator 8, and the power generator 8 generatespower by using shaft power of the rotational shaft. The operating fluidis lowered in pressure and temperature in the expansion module 7, isdischarged from the expansion module 7 and flows into the condenser 9.The operating fluid having flowed into the condenser 9 is cooled bycooling water in the condenser 9 to be converted into an operating fluidof a liquid. That is, the operating fluid condenses. The operating fluidcirculates among the evaporator 4, the expansion module 7 and thecondenser 9 through the operating fluid path 6.

The cooling water is conveyed through the cooling water path 12 by thecooling water pump 11 and is heated by condensation heat of theoperating fluid in the condenser 9. The cooling water discharged fromthe condenser 9 is cooled by the atmospheric air in the cooling tower13. The cooling water circulates between the condenser 9 and the coolingtower 13 through the cooling water path 12.

The blower 14 conveys the atmospheric air introduced by the atmosphereintroducing portion 15 to the cooling tower 13. This atmospheric air isheated in the cooling tower 13 by the condensation heat absorbed by thecooling water. As a result, the condensation heat of the operating fluidis given to the atmospheric air through the cooling water and isreleased to an exterior through the atmospheric air.

A cycle by which the operating fluid circulates is a Rankine cycle. Thepower generating system in FIG. 37 uses two kinds of thermal mediacomposed of the heat source fluid and the operating fluid, and thereforeis called a binary turbine system.

FIG. 38 is a schematic diagram showing a second example representing theconfiguration of the conventional power generating system. In FIG. 38,components identical or similar to those shown in FIG. 37 are referredto as identical signs, and an explanation overlapping the explanation inFIG. 37 is omitted (same in third to sixth examples to be hereinafterdescribed).

The power generating system in FIG. 38 includes the heat source fluidheater 21, the heat source fluid pump 22 and the heat source fluid path23 in addition to the components shown in FIG. 37. In the explanation inFIG. 38, components indicated at signs 1 to 3 are called the first heatsource fluid heater 1, the first heat source fluid pump 2 and the firstheat source fluid path 3, and components indicated at signs 21 to 23 arecalled the second heat source fluid heater 21, the second heat sourcefluid pump 22 and the second heat source fluid path 23. The heat sourcefluid conveyed through the first heat source fluid path 3 is called afirst heat source fluid, and the heat source fluid conveyed through thesecond heat source fluid path 23 is called a second heat source fluid.

The first heat source fluid is conveyed through the first heat sourcefluid path 3 by the first heat source fluid pump 2, and is heated by thefirst heat source fluid heater 1. The first heat source fluid dischargedfrom the first heat source fluid heater 1 flows into the second heatsource fluid heater 21, and is lowered in temperature by heating thesecond heat source fluid in the second heat source fluid heater 21. Thefirst heat source fluid circulates between the first heat source fluidheater 1 and the second heat source fluid heater 21 through the firstheat source fluid path 3.

The second heat source fluid is conveyed through the second heat sourcefluid path 23 by the second heat source fluid pump 22, and is heated bythe second heat source fluid heater 21. An example of the second heatsource fluid is thermal medium oil or water. The second heat sourcefluid discharged from the second heat source fluid heater 21 flows intothe evaporator 4, and is lowered in temperature by heating the operatingfluid in the evaporator 4. The second heat source fluid circulatesbetween the second heat source fluid heater 21 and the evaporator 4through the second heat source fluid path 23.

Here, the power generating system in FIG. 37 and the power generatingsystem in FIG. 38 will be compared.

In FIG. 37, since separated substances are accumulated in the evaporator4 depending upon components contained in the heat source fluid, it isnecessary to frequently disassemble the evaporator 4 for the cleaning.In this case, since the operating fluid path 6 containing a low-boilingmedium of CFC or the like is to be disassembled, the disassembly is notpreferable. On the other hand, in FIG. 38, not the evaporator 4 but thesecond heat source fluid heater 21 is disassembled and cleaned.Therefore, it is not necessary to disassemble the operating fluid path6.

FIG. 39 is a supplementary diagram for explaining the conventional powergenerating system. FIG. 39 shows a part of the power generating systemin each of FIGS. 37 and 38 with the same drawing for descriptivepurposes.

In FIG. 37, the heat source fluid circulates, but as shown in FIG. 39,only passes through the evaporator 4 and does not need to circulate. Inthis case, an example of the heat source fluid is hot spring waterwelling from the ground 10, and the power generating system is notequipped with the heat source fluid heater 1. In a case where the heatsource fluid is the hot spring water, separated substances tend to beeasily accumulated in the evaporator 4 in FIG. 39, and it is necessaryto frequently disassemble the evaporator 4 for the cleaning. On thisoccasion, the operating fluid path 6 is to be disassembled in thisexample.

Likewise, in FIG. 38, the first heat source fluid circulates, but asshown in FIG. 39, only passes through the second heat source fluidheater 21 and does not need to circulate. In this case, an example ofthe first heat source fluid is hot spring water welling from the ground10, and the power generating system is not equipped with the first heatsource fluid heater 1. In a case where the heat source fluid is the hotspring water, separated substances tend to be easily accumulated in thesecond heat source fluid heater 21 in FIG. 39, and it is necessary tofrequently disassemble the second heat source fluid heater 21 for thecleaning. On this occasion, in this example it is not necessary todisassemble the operating fluid path 6.

FIG. 40 is a schematic diagram showing a third example representing theconfiguration of the conventional power generating system.

The power generating system in FIG. 40 does not include the heat sourcefluid heater 1, the heat source fluid pump 2, the heat source fluid path3, the evaporator 4, and the operating fluid pump 5 shown in FIG. 37. Anexample of the operating fluid flowing in the operating fluid path 6 inFIG. 40 is a gas of geothermal steam or the like.

The operating fluid of the gas flows into the expansion module 7 fromthe operating fluid path 6 to drive the rotational shaft of theexpansion module 7. The power generator 8 generates power by using theshaft power of the rotational shaft. The operating fluid is thereafterdischarged to the operating fluid path 6 from the expansion module 7 andflows into the condenser 9. The operating fluid having flowed into thecondenser 9 is cooled by cooling water in the condenser 9 to beconverted into the operating fluid of a liquid, and is returned to theground.

FIG. 41 is a schematic diagram showing a fourth example representing theconfiguration of the conventional power generating system.

The power generating system in FIG. 41 does not include the heat sourcefluid heater 1, the heat source fluid pump 2 and the heat source fluidpath 3 shown in FIG. 37. An example of the evaporator 4 in FIG. 41 is asmall-sized biomass boiler that burns biomass fuel of a wooden chip orthe like, and an example of the operating fluid flowing in the operatingfluid path 6 in FIG. 41 is water of a gas or liquid. In this case, theevaporator 4 heats water of a liquid by combustion exhaust gasesgenerated by burning the biomass fuel, converting the water of theliquid into water (steam) of a gas. Another example of the evaporator 4is a solar energy collector for collecting solar energy, and an exampleof the operating fluid in this case is CFC of a gas or liquid. A furtherother example of the evaporator 4 is an exhaust heat collector thatcollects factory exhaust heat or the like, and an example of theoperating fluid in this case is water of a gas or liquid.

The operating fluid of the liquid is conveyed through the operatingfluid path 6 by the operating fluid pump 5, is heated by the evaporator4, and is converted into the operating fluid of the gas. The operatingfluid discharged from the evaporator 4 flows into the expansion module 7to drive the rotational shaft of the expansion module 7. The powergenerator 8 generates power by using the shaft power of the rotationalshaft. The operating fluid is thereafter discharged from the expansionmodule 7 and flows into the condenser 9. The operating fluid havingflowed into the condenser 9 is cooled by the cooling water in thecondenser 9 to be converted into the operating fluid of the liquid. Theoperating fluid circulates among the evaporator 4, the expansion module7 and the condenser 9 through the operating fluid path 6.

FIG. 42 is a schematic diagram showing a fifth example representing theconfiguration of the conventional cooling system.

The cooling system in FIG. 42 includes the heat source fluid heater 1,the heat source fluid pump 2, the heat source fluid path 3, the coolingwater pump 11, the cooling water path 12, the cooling tower 13, theblower 14, the atmosphere introducing portion 15, a refrigerator 16, acooled fluid pump 17, a cooled fluid path 18, and a cold load 19. Therefrigerator 16 includes a heat absorbing module 16 a, a cooling module16 b and a heat releasing module 16 c. The refrigerator 16 according tothe present embodiment is of an absorption type or adsorption type.

As similar to the case of the first example, the heat source fluid isconveyed through the heat source fluid path 3 by the heat source fluidpump 2, and is heated by the heat source fluid heater 1. The heat sourcefluid discharged from the heat source fluid heater 1 flows into the heatabsorbing module 16 a, and is lowered in temperature by heating the heatabsorbing module 16 a. That is, the heat absorbing module 16 a absorbsheat of the heat source fluid. The heat source fluid circulates betweenthe heat source fluid heater 1 and the heat absorbing module 16 athrough the heat source fluid path 3.

The refrigerator 16 includes the heat absorbing module 16 a, the coolingmodule 16 b and the heat releasing module 16 c, and a cooling medium iscontained in the refrigerator 16. An example of the cooling medium iswater or ammonia. The cooling module 16 b cools a cooled fluid (coolingtarget fluid) by evaporation heat (evaporative latent heat) of thecooling medium. An example of the cooled fluid is water. The heatabsorbing module 16 a uses the heat source fluid to cause the coolingmedium or a substance holding the cooling medium to absorb heat. Theheat absorbing module 16 a, for example, heats an absorption liquid oran adsorption agent having collected the cooling medium from the coolingmodule 16 b by the heat source fluid to vaporize the cooling medium. Theheat releasing module 16 c uses the cooling water to cause the coolingmedium or a substance holding the cooling medium to release heat. Theheat releasing module 16 c, for example, cools the adsorption agentcollecting the cooling medium by the cooling water or cools the coolingmedium vaporized from the absorption liquid or the adsorption agent bythe cooling water to liquidize (condense) the cooling medium. In thisway, the heat releasing module 16 c releases the heat received from thecooled fluid and the heat absorbed by the heat absorbing module 16 a tothe cooling water. The cooling module 16 b cools the cooled fluid byusing the cooling medium from the heat releasing module 16 c.

The cooled fluid is conveyed through the cooled fluid path 18 by thecooled fluid pump 17, and is cooled by the cooling module 16 b. Thecooled fluid discharged from the cooling module 16 b flows into the coldload 19, and is increased in temperature by cooling the cold load 19. Anexample of the cold load 19 is cooling target facilities such asbuilding cooling or cooling target devices such as server computers. Thecooled fluid in the former case is used in cold water for cold heatsource in cooling air-conditioning. The cooled fluid circulates betweenthe cooling module 16 b and the cold load 19 through the cooled fluidpath 18.

The cooling water is conveyed through the cooling water path 12 by thecooling water pump 11, and is increased in temperature by cooling theheat releasing module 16 c. The cooling water discharged from the heatreleasing module 16 c is cooled by the atmospheric air in the coolingtower 13. The cooling water circulates between the heat releasing module16 c and the cooling tower 13 through the cooling water path 12.

The blower 14 conveys the atmospheric air introduced by the atmosphereintroducing portion 15 to the cooling tower 13. This atmospheric air isheated in the cooling tower 13 by the heat absorbed by the coolingwater. As a result, the potential heat of the heat source fluid or thecooled fluid is given to the atmospheric air through the cooling waterand is released to an exterior through the atmospheric air.

FIG. 43 is a schematic diagram explaining an operation of therefrigerator 16 in FIG. 42.

As shown in FIG. 43, the heat absorbing module 16 a absorbs enthalpy H₁from the heat source fluid, and the cooling module 16 b absorbs enthalpyH₂ from the cooled fluid. The heat releasing module 16 c releasesenthalpy H₃ to the cooling water. A relation of H₁+H₂=H₃ is establishedbetween enthalpy H₁ to H₃. An example of a ratio of enthalpy H₁ to H₃ isH₁:H₂:H₃=1.0:0.6:1.6. This explanation can be applied not only to therefrigerator 16 in FIG. 42 but also to the refrigerator in FIG. 44.

FIG. 44 is a schematic diagram showing a sixth example representing theconfiguration of the conventional cooling system.

The cooling system in FIG. 44 includes the heat source fluid heater 21,the heat source fluid pump 22 and the heat source fluid path 23 inaddition to the components shown in FIG. 42. In the explanation in FIG.44, as similar to the case in the second example, the first heat sourcefluid heater 1, the first heat source fluid pump 2, the first heatsource fluid path 3, the second heat source fluid heater 21, the secondheat source fluid pump 22, and the second heat source fluid path 23 areadopted as titles. The heat source fluid in the first heat source fluidpath 3 is called a first heat source fluid, and the heat source fluid inthe second heat source fluid path 23 is called a second heat sourcefluid.

The first heat source fluid is heated by the first heat source fluidheater 1, and is lowered in temperature by heating the second heatsource fluid in the second heat source fluid heater 21. The second heatsource fluid is heated by the second heat source fluid heater 21, and islowered in temperature by heating the heat absorbing module 16 a. Thatis, the heat absorbing module 16 a absorbs heat of the second heatsource fluid.

Here, the cooling system in FIG. 42 and the cooling system in FIG. 44will be compared.

In FIG. 42, since separated substances are accumulated in therefrigerator 16 (heat absorbing module 16 a) depending upon componentscontained in the heat source fluid, it is necessary to frequentlydisassemble the refrigerator 16 for the cleaning, but the disassembly ofthe refrigerator 16 is not preferable. On the other hand, in FIG. 44,not the refrigerator 16 but the second heat source fluid heater 21 isdisassembled and cleaned, and therefore, it is not necessary todisassemble the refrigerator 16.

FIG. 45 is a supplementary diagram for explaining the conventionalcooling system. FIG. 45 shows a part of the cooling system in each ofFIG. 42 and FIG. 44 with the same drawing for descriptive purposes.

In FIG. 42, the heat source fluid circulates, but as shown in FIG. 45,only passes through the refrigerator 16 (heat absorbing module 16 a) anddoes not need to circulate. This is the same with the first example. Inthis case, since separated substances of the hot spring water (heatsource fluid) tend to be easily accumulated in the refrigerator 16 inFIG. 45, it is necessary to frequently disassemble the refrigerator 16for the cleaning.

Likewise, in FIG. 44, the first heat source fluid circulates, but asshown in FIG. 45, only passes through the second heat source fluidheater 21 and does not need to circulate. This is the same with thesecond example. In this case, since separated substances of the hotspring water (first heat source fluid) tend to be easily accumulated inthe second heat source fluid heater 21 in FIG. 45, it is necessary tofrequently disassemble the second heat source fluid heater 21 for thecleaning. However, it is not necessary to disassemble the refrigerator16.

FIG. 46 is a schematic diagram showing a first specific example of therefrigerator 16 in FIG. 42.

The refrigerator 16 in FIG. 46 is of an absorption type, and includes anevaporator 16 d ₁, a condenser 16 d ₂, an absorber 16 d ₃, and aregenerator 16 d ₄.

A cooling medium of a liquid is supplied to the evaporator 16 d ₁ from aflow path N₁. Since an atmosphere in the evaporator 16 d ₁ is set to alow pressure, the cooling medium vaporizes in the evaporator 16 d ₁. Theevaporator 16 d ₁ cools a cooled fluid from the cooled fluid path 18 byevaporation heat of the cooling medium, and discharges the coolingmedium of a gas to a flow path N₂. The evaporator 16 d ₁ corresponds tothe aforementioned cooling module 16 b.

A cooling medium of a gas is supplied to the absorber 16 d ₃ from theflow path N₂. The absorber 16 d ₃ causes an absorption liquid from aflow path N₄ to absorb the cooling medium, and discharges the absorptionliquid containing the cooling medium to a flow path N₃. In this case, anexample of a combination of the cooling medium and the absorption liquidis ammonia and water.

The absorption liquid containing the cooling medium is supplied to theregenerator 16 d ₄ from the flow path N₃. The regenerator 16 d ₄ heatsthe absorption liquid by the heat source fluid from the heat sourcefluid path 3. As a result, the cooling medium is released from theabsorption liquid to vaporize. The absorption liquid having released thecooling medium is discharged to the flow path N₄ and the vaporizedcooling medium is discharged to a flow path N₅. The regenerator 16 d ₄corresponds to the aforementioned heat absorbing module 16 a, and causesthe cooling medium to absorb heat by using the heat source fluid.

A cooling medium of a gas is supplied to the condenser 16 d ₂ from theflow path N₅. The condenser 16 d ₂ cools the cooling medium by thecooling water from the cooling water path 12 and liquidizes (condenses)the cooling medium. The liquidized solvent is discharged to the flowpath N₁. The condenser 16 d ₂ corresponds to the aforementioned heatreleasing module 16 c, and causes the cooling medium to release heat byusing the cooling water.

FIGS. 47 and 48 are schematic diagrams each showing a second specificexample of the refrigerator 16 in FIG. 42.

FIGS. 47 and 48 show different states of the same refrigerator 16. Therefrigerator 16 is of an adsorption type, and includes an evaporator 16e ₁, a condenser 16 e ₂, a first heat exchanger 16 e ₃, a second heatexchanger 16 e ₄, a first inlet valve 16 e ₅, a second inlet valve 16 e₆, a first outlet valve 16 e ₇, a second outlet valve 16 e ₈, and acooling medium pump 16 e ₉. The refrigerator 16 is operable toalternately repeat the state in FIG. 47 and the state in FIG. 48.

In FIG. 47, the first inlet valve 16 e ₅ and the second outlet valve 16e ₈ are opened, and the second inlet valve 16 e ₆ and the first outletvalve 16 e ₇ are closed. In addition, a valve 12 a in the cooling waterpath 12 is set to supply the cooling water to the first heat exchanger16 e ₃ and the condenser 16 e ₂, and a valve 3 a in the heat sourcefluid path 3 is set to supply the heat source fluid to the second heatexchanger 16 e ₄.

A cooling medium of a liquid is supplied to the evaporator 16 e ₁ inFIG. 47 from a flow path M₁ by the cooling medium pump 16 e ₉. Anexample of the cooling medium in this case is water. Since an atmospherein the evaporator 16 e ₁ is set to a low pressure, the cooling mediumvaporizes in the evaporator 16 e ₁. The evaporator 16 e ₁ cools a cooledfluid from the cooled fluid path 18 by evaporation heat of the coolingmedium. The vaporized cooling medium flows into the first heat exchanger16 e ₃ through the first inlet valve 16 e ₅ and the cooling mediumstaying in the liquid state is accumulated in a reserving module K₁. Thecooling medium accumulated in the reserving module K₁ again flows intothe flow path M₁ from a flow path M₂. The evaporator 16 e ₁ correspondsto the aforementioned cooling module 16 b.

The first heat exchanger 16 e ₃ in FIG. 47 includes a first absorptionagent K₃, and a cooling medium of a gas is supplied to the first heatexchanger 16 e ₃ from the first inlet valve 16 e ₅. The first absorptionagent K₃ adsorbs this cooling medium to generate adsorption heat. Thefirst heat exchanger 16 e ₃ absorbs this adsorption heat by the coolingwater from the cooling water path 12. The first heat exchanger 16 e ₃ inthis case corresponds to the aforementioned heat releasing module 16 c,and uses the cooling water to cause a substance (adsorption agent)holding the cooling medium to release heat.

The second heat exchanger 16 e ₄ in FIG. 47 includes a second absorptionagent K₄. The second absorption agent K₄ has already adsorbed thecooling medium at the previous state shown in FIG. 48. Therefore, whenthe second absorption agent K₄ is heated by the heat source fluid fromthe heat source fluid path 3, the cooling medium is desorbed from thesecond absorption agent K₄ to vaporize the cooling medium. The vaporizedcooling medium flows into the condenser 16 e ₂ through the second outletvalve 16 e ₈. The second heat exchanger 16 e ₄ in this case correspondsto the aforementioned heat absorbing module 16 a, and uses the heatsource fluid to cause a substance (adsorption agent) holding the coolingmedium to absorb the heat.

A cooling medium of a gas is supplied to the condenser 16 e ₂ in FIG. 47from the second outlet valve 16 e ₈. The condenser 16 e ₂ cools thecooling medium by the cooling water from the cooling water path 12 toliquidize (condense) the cooling medium. The liquidized solvent isaccumulated in the reserving module K₂. The cooling medium accumulatedin the reserving module K₂ again flows into the flow path M₁ from a flowpath M₃. The condenser 16 e ₂ corresponds to the aforementioned heatreleasing module 16 c, and uses the cooling water to release heat of thecooling medium.

On the other hand, in FIG. 48 the first inlet valve 16 e ₅ and thesecond outlet valve 16 e ₈ are closed, and the second inlet valve 16 e ₆and the first outlet valve 16 e ₇ are opened. In addition, the valve 12a in the cooling water path 12 is set to supply the cooling water to thesecond heat exchanger 16 e ₄ and the condenser 16 e ₂, and a valve 3 ain the heat source fluid path 3 is set to supply the heat source fluidto the first heat exchanger 16 e ₃.

The operations of the evaporator 16 e ₁, the condenser 16 e ₂, the firstheat exchanger 16 e ₃, and the second heat exchanger 16 e ₄ in FIG. 48are respectively similar to the operations of the evaporator 16 e ₁, thecondenser 16 e ₂, the second heat exchanger 16 e ₄, and the first heatexchanger 16 e ₃ in FIG. 47. That is, in FIGS. 47 and 48, roles of thefirst heat exchanger 16 e ₃ and the second heat exchanger 16 e ₄ arereversed. As a result, the first and second adsorption agents K₃, K₄alternately repeat adsorption and desorption of the cooling medium.

In general, the absorption type refrigerator 16 has an advantage thatthe cooling performance is high and an advantage that noises to begenerated are small. On the other hand, the adsorption type refrigerator16 has an advantage that a low-temperature heat source fluid tends to beeasily used.

The explanation in FIGS. 46 to 48 can be applied to the refrigerator 16in FIG. 44 when the heat source fluid path 3 is replaced by a heatsource fluid path 23.

BRIEF DESCRIPTION OF THE DRAWINGS

FIGS. 1 to 8 are schematic diagrams showing the configuration of a powergenerating system according to each of first to eighth embodiments;

FIGS. 9 and 10 are schematic diagrams each showing the configuration ofa power generating system according to each of a ninth embodiment and amodification thereof;

FIGS. 11 and 12 are schematic diagrams each showing the configuration ofa power generating system according to each of a tenth embodiment and amodification thereof;

FIGS. 13 to 24 are schematic diagrams each showing the configuration ofa power generating system according to each of eleventh to twenty-secondembodiments;

FIGS. 25 to 32 are schematic diagrams each showing the configuration ofa cooling system according to each of twenty-third to thirtiethembodiments;

FIGS. 33 and 34 are schematic diagrams each showing the configuration ofa cooling system according to each of a thirty-first embodiment and amodification thereof;

FIGS. 35 and 36 are schematic diagrams each showing the configuration ofa cooling system according to each of a thirty-second embodiment and amodification thereof;

FIGS. 37 and 38 are schematic diagrams showing first and second examplesrepresenting the configuration of a conventional power generatingsystem;

FIG. 39 is a supplementary diagram explaining the conventional powergenerating system;

FIGS. 40 and 41 are schematic diagrams showing third and fourth examplesrepresenting the configuration of the conventional power generatingsystem;

FIG. 42 is a schematic diagram showing a fifth example representing theconfiguration of a conventional cooling system;

FIG. 43 is a schematic diagram explaining an operation of a refrigeratorin FIG. 42;

FIG. 44 is a schematic diagram showing a sixth example representing theconfiguration of the conventional cooling system;

FIG. 45 is a supplementary diagram explaining the conventional coolingsystem;

FIG. 46 is a schematic diagram showing a first specific example of therefrigerator in FIG. 42;

FIGS. 47 and 48 are schematic diagrams showing a second specific exampleof the refrigerator in FIG. 42;

FIG. 49 is a supplementary diagram explaining the power generatingsystem according to the first embodiment; and

FIG. 50 is a supplementary diagram explaining a cooling system accordingto a twenty-third embodiment.

DETAILED DESCRIPTION

Embodiments will now be explained with reference to the accompanyingdrawings.

In turbine power generation using hot spring heat, solar energy, asmall-sized biomass boiler, factory exhaust heat, geothermal steam andthe like as heat sources, a difference in temperature across theevaporator 4 is small, and a difference in pressure across the expansionmodule 7 is small. Further, since the expansion module 7 is small insize, a power generation coefficient or an energy utilization rate ofthe power generating system is low.

The power generation coefficient is a ratio between thermal energy givento an operating fluid by the evaporator 4 and electrical energygenerated by the power generator 8 (refer to the first, second andfourth examples). However, the power generation coefficient of the thirdexample is a ratio between the thermal energy that the operating fluidfirst has and the electrical energy generated by the power generator 8.

In addition, the ratio called the energy utilization rate in the presentspecification is a ratio between thermal energy given to a heat sourcefluid by the heat source fluid heater 1 and energy used by the powergenerating system (refer to the first and second examples). However, theenergy utilization rate of the third example is a ratio between thethermal energy that the operating fluid first has and the energy used bythe power generating system. In addition, the energy utilization rate ofthe fourth example is a ratio between the thermal energy given to theoperating fluid by the evaporator 4 and the energy used by the powergenerating system. The conventional example of the energy used by thepower generating system is electrical energy generated by the powergenerator 8.

For example, the power generation coefficient of each of the first tofourth examples is 10% or less, and 90% or more of the thermal energygiven to the operating fluid is released to the cooling water as thecondensation heat of the operating fluid. However, a temperature of thecooling water having collected the condensation heat is low, and the usevalue is low. For example, in a case of having collected thecondensation heat by using tap water as cooling water, a temperature ofthe cooling water is approximately 30° C. Therefore, the condensationheat of the operating fluid in the first to fourth examples isdiscarded.

For example, in the power generating system (first example) in FIG. 37,when the thermal energy given to the operating fluid by the evaporator 4is assumed to be 100, the thermal energy given to the heat source fluidby the heat source fluid heater 1 is approximately 100. In addition, therotational energy of the expansion module 7 is approximately 10, and theelectrical energy generated by the power generator 8 is approximately10. However, consumption power of pumps 2, 5, 11 or the blower 14 willbe ignored. Thereby, the power generation coefficient becomesapproximately 10% (10/100), and the energy utilization rate becomesapproximately 10% (10/100). This is the same as in the power generatingsystems (second to fourth examples) in FIG. 38, FIGS. 40 and 41.

In this way, in the turbine power generation using the hot spring heat,the solar energy, the small-sized biomass boiler, the factory exhaustheat, the geothermal steam and the like as the heat sources, a lot ofthe energy is wasteful. Therefore, it is preferable that the energyutilization rate of the power generating system is improved to reducethe waste of the energy.

In addition, in the cooling system in FIG. 42 or FIG. 44, the heat ofthe heat source fluid or the cooled fluid is given to the cooling waterby the refrigerator 16, and the heat of the cooling water is discardedto the atmospheric air in the cooling tower 13. In this way, in theconventional cooling system, in many cases the exhaust heat of therefrigerator 16 is discarded to the atmospheric air. The reason is thata temperature of the cooling water having absorbed the heat of the heatsource fluid or the cooled fluid is not high and the heat of the coolingwater is low-quality heat, and therefore, a value of using the heat ofthe cooling water is low.

In the refrigerator 16 using the hot spring heat, the solar energy, thesmall-sized biomass boiler, the factory exhaust heat and the like as theheat sources, the temperature of the heat source fluid is low.Therefore, COP (COP: coefficient of performance) of the refrigerator 16becomes smaller. COP is found by dividing an absolute value E2 of thecold heat produced by the refrigerator 16 by heat E1 used in a drive ofthe refrigerator 16 (COP=E2/E1). On the other hand, exhaust heat E3 ofthe refrigerator 16 is an addition of the absolute value E2 of the coldheat and the drive heat E1 (E3=E1+E2). Accordingly, the exhaust heat E3of the refrigerator 16 is represented according to the following formula(1).

E3=E2 (1/COP+1)   (1)

In this way, when the refrigerator 16 produces the cold heat, theexhaust heat E3 greater than the absolute value E2 of the cold heat isgenerated. Therefore, it is desirable that this low-quality exhaust heatE3 is not put aside but is effectively used.

In one embodiment, an exhaust heat collecting system of collectingexhaust heat in a fluid treatment system. The fluid treatment systemincludes a fluid path configured to include at least an operating fluidpath or a cooled fluid path among a first heat source fluid path, asecond heat source fluid path, the operating fluid path and the cooledfluid path, the first heat source fluid path conveying a first heatsource fluid, the second heat source fluid path conveying a second heatsource fluid heated by heat of the first heat source fluid, theoperating fluid path conveying an operating fluid, the cooled fluid pathconveying a cooled fluid, the operating fluid being conveyed through ornot through an evaporator that vaporizes the operating fluid by usingthe first or second heat source fluid, the cooled fluid being conveyedthrough a cooling module that cools the cooled fluid. The fluidtreatment system further includes a fluid treatment module configured toinclude an expansion module that rotates and drives to expand theoperating fluid, a power generator that is connected to a rotationalshaft of the expansion module, and a condenser that condenses theoperating fluid, or configured to include a heat absorbing module thatabsorbs heat of the first or second heat source fluid, and a heatreleasing module that releases heat received from the cooled fluid andheat absorbed by the heat absorbing module. The exhaust heat collectingsystem includes a water path configured to supply water to the condenseror the heat releasing module, heat the water by the condensation in thecondenser or by the heat release in the heat releasing module, andconvey the water of a first temperature discharged from the condenser orthe heat releasing module. The exhaust heat collecting system furtherincludes a heater configured to heat the water from the water path byusing the first heat source fluid, the second heat source fluid or theoperating fluid to produce the water of a second temperature to be usedas hot water or to produce steam.

In FIGS. 1 to 36, 49 and 50, components identical or similar to those inFIGS. 37 to 48 are referred to as identical signs, and an explanationoverlapping the explanation in FIGS. 37 to 48 is omitted.

First Embodiment

FIG. 1 is a schematic diagram showing the configuration of a powergenerating system according to a first embodiment.

The power generating system in FIG. 1, as similar to the powergenerating system in FIG. 37, includes the heat source fluid heater 1,the heat source fluid pump 2, the heat source fluid path 3, theevaporator 4, the operating fluid pump 5, the operating fluid path 6,the expansion module 7, the power generator 8 and the condenser 9. Thepower generating system in FIG. 1 further includes a heater 31, a hotwater tank 32, a water pump 33, and a water path 34 configuring anexhaust heat collecting system of collecting the exhaust heat of thepower generating system.

The heat source fluid (first heat source fluid) is conveyed through theheat source fluid path 3 by the heat source fluid pump 2, and is heatedby the heat source fluid heater 1. The heat source fluid according tothe present embodiment is heated in the heat source fluid heater 1obtaining heat from a heat source of non-fossil fuel. An example of thisheat source fluid heater 1 includes a small-sized biomass boiler usingbiomass fuel as the heat source, a solar energy collector using solarenergy as the heat source, an exhaust heat collector using factoryexhaust heat as the heat source, and the like. The factory exhaust heatitself can be generally obtained from fossil fuel, but the fossil fuelis burned not in the heat source fluid heater 1, but outside of the heatsource fluid heater 1. Therefore, the factory exhaust heat is alsoclassified into the heat source in the non-fossil fuel. The heat sourcefluid discharged from the heat source fluid heater 1 flows into theevaporator 4, and is lowered in temperature by heating the operatingfluid in the evaporator 4.

The heat source fluid in the present embodiment, as shown in FIG. 39,may be hot spring water springing forth from the ground 10. In thiscase, the power generating system in

FIG. 1 may not include the heat source fluid heater 1. The heat sourcefluid in the present embodiment may circulate as shown in FIG. 37 or maynot circulate as shown in FIG. 39. This is the same as in second totenth embodiments to be described later.

The operating fluid of the liquid is conveyed through the operatingfluid path 6 by the operating fluid pump 5, is heated by the evaporator4, and is converted in phase into the operating fluid of the gas. Anexample of the operating fluid is a low-boiling medium of CFC or thelike. The operating fluid discharged from the evaporator 4 flows intothe expansion module 7 and expands in the expansion module 7 to drive arotational shaft of the expansion module 7. The rotational shaft of theexpansion module 7 is connected to the power generator 8, and the powergenerator 8 generates power by using the shaft power of the rotationalshaft. The operating fluid is lowered in pressure and temperature in theexpansion module 7, is discharged from the expansion module 7 and flowsinto the condenser 9. The operating fluid having flowed into thecondenser 9 is cooled by water in the condenser 9 to be converted inphase into an operating fluid of the liquid.

The water is conveyed through the water path 34 by the water pump 33 andis heated by condensation heat of the operating fluid in the condenser9. The water discharged from the condenser 9 is conveyed through thewater path 34, and is supplied to the heater 31.

The heater 31 is provided in the heat source fluid path 3. The heater 31heats the water from the water path 34 by using the heat source fluid ofthe heat source fluid path 3 and produces water to be used as hot water.The hot water is conveyed through the water path 34 and is reserved inthe hot water tank 32. The heater 31 in the present embodiment heats thewater by using the heat source fluid flowing downstream of theevaporator 4. The heat source fluid discharged from the evaporator 4flows into the heater 31, and is lowered in temperature by heating thewater in the heater 31. The heat source fluid circulates among the heatsource fluid heater 1, the evaporator 4 and the heater 31 through theheat source fluid path 3.

In the present embodiment, the condensation heat discharged in thecondenser 9 is given to the water before being heated by the heater 31without being given to the cooling tower 13. An example of the waterincludes tap water. In addition, a temperature of the reserved hot wateris made to, for example, 60° C. estimated as a generally usable hotwater temperature. This hot water is effectively used in bathingfacilities, for dish washing in restaurants, and the like. In a case ofusing the hot water in linen laundry in hospitals, it is preferable toheat the hot water to 80° C. In the present embodiment, since there isno heat put aside externally, the energy utilization rate improves to100%.

Here, a temperature of water in the water pump 33 is set to 15° C., atemperature of water heated by the condenser 9 is set to 30° C., and atemperature of water heated by the heater 31 is set to 60° C. 30° C. isset in the example of the first temperature, and 60° C. is set in theexample of the second temperature.

In this case, when the thermal energy given to the heat source fluid bythe heat source fluid heater 1 is assumed to be 100, electrical energygenerated by the power generator 8, thermal energy given to water by thecondenser 9 and thermal energy given to water by the heater 31 arerespectively 3.6, 32.1 and 4.3. Accordingly, the energy utilization ratebecomes 100% ((3.6+32.1+64.3)/100).

FIG. 49 is a supplementary diagram explaining the power generatingsystem according to the first embodiment.

The power generating system in FIG. 49 includes the components shown inFIG. 1, and besides, the cooling water pump 11, the cooling water path12, the cooling tower 13, the blower 14, and the atmosphere introducingportion 15.

In FIG. 49, the water in the water path 34 is heated only by the heater31, and is not heated in the condenser 9. The condensation heatdischarged in the condenser 9 is put aside externally. In this case, theenergy utilization rate by the above-mentioned numerical example becomes68% ((3.6+64.3)/100).

As described above, the power generating system according to the presentembodiment uses the heat source fluid from the heat source fluid path 3to heat the water of the first temperature and produce the water of thesecond temperature to be used as the hot water. Therefore, according tothe present embodiment, it is possible to improve the energy utilizationrate in the power generating system.

The present embodiment is applicable even if the heat source in the heatsource fluid heater 1 is a high-temperature heat source, but iseffectively applicable in a case where the heat source in the heatsource fluid heater 1 is a low-temperature heat source such as biomassfuel, solar energy, factory exhaust heat and hot spring heat. Further,the present embodiment is effectively applicable in any heat source in acase where a temperature of the heat source fluid in an inlet of theevaporator 4 is 200° C. or less. This is true of second to twenty-secondembodiments to be described later. The reason is that in a case wherethe heat source in the heat source fluid heater 1 is a low-temperatureheat source, the power generation coefficient is lower, and the energyutilization rate in a case where the present embodiment is not appliedis low. According to the present embodiment, it is possible toremarkably improve the energy utilization rate in a case where the heatsource in the heat source fluid heater 1 is the low-temperature heatsource. This is true of the second to twenty-second embodiments to bedescribed later.

In addition, the configuration of the present embodiment is effectivelyapplicable in a case where the maximum temperature of the heat sourcefluid in the heat source fluid path 3 is 200° C. or less.

In addition, the heater 31 may produce steam instead of producing thewater to be used as the hot water. That is, the heater 31 may producewater of a gas instead of producing the water of the liquid. In thiscase, the hot water tank 32 is replaced by, for example, a facility forreserving, conveying or using the steam. This is true of the second totwenty-second embodiments to be described later (however, in the fourthand twentieth embodiments, a heat use destination 37 is replaced by, forexample, a facility for reserving, conveying or using the steam).

Second Embodiment

FIG. 2 is a schematic diagram showing the configuration of a powergenerating system according to a second embodiment. In FIG. 2,components identical or similar to those in FIG. 1 are referred to asidentical signs, and an explanation overlapping the explanation in FIG.1 is omitted. This is true mutually between FIGS. 1 to 36.

The heater 31 in the first embodiment, as shown in FIG. 1, heats thewater by using the heat source fluid flowing downstream of theevaporator 4. On the other hand, the heater 31 in the second embodiment,as shown in FIG. 2, heats the water by using the heat source fluidflowing upstream of the evaporator 4.

In the present embodiment, a temperature of the heat source fluid in theinlet of the heater 31 is higher than a temperature of the heat sourcefluid in the inlet of the evaporator 4. Therefore, according to thepresent embodiment, the water tends to be easily heated to a highertemperature. On the other hand, according to the first embodiment, it ispossible to use more percentage of thermal energy for the powergeneration by the power generator 8.

Third Embodiment

FIG. 3 is a schematic diagram showing the configuration of a powergenerating system according to a third embodiment.

The evaporator 4 and the heater 31 in the first and second embodimentsare, as shown in FIG. 1 and FIG. 2, arranged in series to the flow ofthe heat source fluid. On the other hand, the evaporator 4 and theheater 31 in the third embodiment are, as shown in FIG. 3, arranged inparallel to the flow of the heat source fluid.

The heat source fluid path 3 in FIG. 3 is branched into a first branchflow path 35 provided with the evaporator 4 and a second branch flowpath 36 provided with the heater 31. The first and second branch flowpaths 35, 36 are branched from a single flow path L₁ at a first point P₁and merge into the single flow path L₁ at a second point P₂.

In the present embodiment, a temperature of the heat source fluid in theinlet of the heater 31 is equal to a temperature of the heat sourcefluid in the inlet of the evaporator 4. Therefore, according to thepresent embodiment, both of the operating fluid and the water tend to beeasily heated to a high temperature.

Fourth Embodiment

FIG. 4 is a schematic diagram showing the configuration of a powergenerating system according to a fourth embodiment.

In FIG. 4, the hot water tank 32 is replaced by the heat use destination37, and the water path 34 is replaced by a circulation water path 38.

The water in the present embodiment is conveyed through the circulationwater path 38 by the water pump 33, and is heated by the condensationheat of the operating fluid in the condenser 9. The water dischargedfrom the condenser 9 is conveyed through the circulation water path 38,and is supplied to the heater 31. The heater 31 uses the heat sourcefluid from the heat source fluid path 3 to heat this water and producewater to be used as the hot water. The hot water is conveyed through thecirculation water path 38 to be supplied to the heat use destination 37.

An example of the heat use destination 37 includes floor heating. Thewater supplied to the heat use destination 37 is lowered in temperatureby being used as the heat source in the heat use destination 37. Thewater discharged from the heat use destination 37 is conveyed throughthe circulation water path 38 to be again supplied to the condenser 9.In this way, the water in the present embodiment circulates through thecirculation water path 38 among the condenser 9, the heater 31 and theheat use destination 37. In a case of supplying the steam to the heatuse destination 37 instead of the hot water, an example of the heat usedestination 37 includes steam heating.

In a case of using the hot water in bathing facilities or for dishwashing in restaurants, the hot water is disposable. On the other hand,in a case of using the hot water for floor heating, the hot water can berepeatedly used. As a result, in the present embodiment, a limitedamount of water can be repeatedly used by circulating the water throughthe circulation water path 38. The heat use destination 37 may befacilities other than the floor heating or the steam heating.

Fifth Embodiment

FIG. 5 is a schematic diagram showing the configuration of a powergenerating system according to a fifth embodiment.

The heat source fluid path 3 in FIG. 5 includes a first bypass flow path44 bypassing a first flow path provided with the evaporator 4, and asecond bypass flow path 48 bypassing a second flow path provided withthe heater 31. The heat source fluid path 3 in FIG. 5 is provided with aplurality of valves 41 to 43 and 45 to 47.

The first bypass flow path 44 is branched from the flow path L₁ at thefirst point P₁ and merges into the flow path L₁ at a third point P₃. Theflow path L₁ between the first point P₁ and the third point P₃ is theabove-mentioned first flow path. The valve 41 is provided in the firstflow path between the first point P₁ and the evaporator 4. The valve 42is provided in the first flow path between the evaporator 4 and thethird point P₃. The valve 43 is provided in the first bypass flow path44.

The second bypass flow path 48 is branched from the flow path L₁ at afourth point P₄ and merges into the flow path L₁ at the second point P₂.The flow path L₁ between the fourth point P₄ and the second point P₂ isthe above-mentioned second flow path. The valve 45 is provided in thesecond flow path between the fourth point P₄ and the heater 31. Thevalve 46 is provided in the second flow path between and the heater 31and the second point P₂. The valve 47 is provided in the second bypassflow path 48.

In the present embodiment, upon performing both of the power generationand the hot water production, the valves 41, 42, 45, 46 are opened andthe valves 43, 47 are closed. In this case, the water is heated by thecondenser 9 and the heater 31 to be a high-temperature hot water.

In addition, upon performing only the power generation, the valves 41,42, 47 are opened and the valves 43, 45, 46 are closed. In this case,the water is heated only by the condenser 9 to be a low-temperature hotwater.

In addition, upon performing only the hot water production, the valves43, 45, 46 are opened and the valves 41, 42, 47 are closed. In thiscase, the water is heated only by the heater 31. Therefore, in a case ofproducing the high-temperature hot water without lowering thetemperature under this condition, a producing amount of the hot water ismade small.

As described above, according to the present embodiment, it is possibleto select three kinds of operations in regard to the power generationand the hot water production by using the first and second bypass flowpaths 44, 48. In the present embodiment, two kinds of operations may beselected by providing only one of the first and second bypass flow paths44, 48 to the power generating system.

Sixth Embodiment

FIG. 6 is a schematic diagram showing the configuration of a powergenerating system according to a sixth embodiment.

The power generating system in FIG. 6 includes the components shown inFIG. 3, and besides, includes a plurality of valves 51 to 54. The valve51 is provided in the first branch flow path 35 between the first pointP₁ and the evaporator 4. The valve 52 is provided in the first branchflow path 35 between the evaporator 4 and the second point P₂. The valve53 is provided in the second branch flow path 36 between the first pointP₁ and the heater 31. The valve 54 is provided in the second branch flowpath 36 between the heater 31 and the second point P₂.

In the present embodiment, upon performing both of the power generationand the hot water production, the valves 51 to 54 are opened. In thiscase, the water is heated by the condenser 9 and the heater 31 to be ahigh-temperature hot water.

In addition, upon performing only the power generation, the valves 51,52 are opened and the valves 53, 54 are closed. In this case, the wateris heated only by the condenser 9 to be a low-temperature hot water.

In addition, upon performing only the hot water production, the valves53, 54 are opened and the valves 51, 52 are closed. In this case, thewater is heated only by the heater 31. Therefore, in a case of producingthe high-temperature hot water without lowering the temperature underthis condition, a producing amount of the hot water is made small.

As described above, according to the present embodiment, it is possibleto select three kinds of operations in regard to the power generationand the hot water production by using the first and second branch flowpaths 37, 38. In the present embodiment, two kinds of operations may beselected by providing only one of a pair of the valves 51, 52 and a pairof the valves 53, 54 to the power generating system.

Seventh Embodiment

FIG. 7 is a schematic diagram showing the configuration of a powergenerating system according to a seventh embodiment.

The power generating system in FIG. 7 includes the heat source fluidheater 21, the heat source fluid pump 22 and the heat source fluid path23 in addition to the components shown in FIG. 1. In the explanation inFIG. 7, as similar to the explanation in FIG. 38, titles of the firstheat source fluid heater 1, the first heat source fluid pump 2 and thefirst heat source fluid path 3, the second heat source fluid heater 21,the second heat source fluid pump 22, and the second heat source fluidpath 23 are adopted. In addition, the heat source fluid of the firstheat source fluid path 3 is called a first heat source fluid, and theheat source fluid of the second heat source fluid path 23 is called asecond heat source fluid.

The first heat source fluid is conveyed through the first heat sourcefluid path 3 by the first heat source fluid pump 2, and is heated by thefirst heat source fluid heater 1. The first heat source fluid dischargedfrom the first heat source fluid heater 1 flows into the second heatsource fluid heater 21, and is lowered in temperature by heating thesecond heat source fluid in the second heat source fluid heater 21.

The second heat source fluid is conveyed through the second heat sourcefluid path 23 by the second heat source fluid pump 22, and is heated bythe second heat source fluid heater 21. The second heat source fluiddischarged from the second heat source fluid heater 21 flows into theevaporator 4, and is lowered in temperature by heating the operatingfluid in the evaporator 4.

The operating fluid of the liquid is conveyed through the operatingfluid path 6 by the operating fluid pump 5, is heated by the evaporator4, and is converted in phase into the operating fluid of the gas. Anexample of the operating fluid is a low-boiling medium of CFC or thelike. The operating fluid discharged from the evaporator 4 flows intothe expansion module 7 and expands in the expansion module 7 to drivethe rotational shaft of the expansion module 7. The rotational shaft ofthe expansion module 7 is connected to the power generator 8, and thepower generator 8 generates power by using the shaft power of therotational shaft. The operating fluid is lowered in pressure andtemperature in the expansion module 7, is discharged from the expansionmodule 7 and flows into the condenser 9. The operating fluid havingflowed into the condenser 9 is cooled by water in the condenser 9 to beconverted in phase into the operating fluid of the liquid.

The water is conveyed through the water path 34 by the water pump 33 andis heated by condensation heat of the operating fluid in the condenser9. The water discharged from the condenser 9 is conveyed through thewater path 34, and is supplied to the heater 31.

In the present embodiment, the heater 31 is provided in the second heatsource fluid path 23. The heater 31 heats the water from the water path34 by using the second heat source fluid and produces water to be usedas hot water. The hot water is conveyed through the water path 34 and isreserved in the hot water tank 32. The heater 31 in the presentembodiment heats the water by using the second heat source fluid flowingdownstream of the evaporator 4. The second heat source fluid dischargedfrom the evaporator 4 flows into the heater 31, and is lowered intemperature by heating the water in the heater 31. The second heatsource fluid circulates among the second heat source fluid heater 21,the evaporator 4 and the heater 31 through the second heat source fluidpath 23.

Here, the power generating system in FIG. 1 and the power generatingsystem in FIG. 7 will be compared.

In FIG. 1, since separated substances are accumulated in the evaporator4 or the heater 31 depending upon components contained in the heatsource fluid, it is necessary to frequently disassemble the evaporator 4or the heater 31 for the cleaning. In this case, the operating fluidpath 6 containing a low-boiling medium such as CFC or the water path 34used in bathing facilities or for dish washing in restaurants will bedisassembled, but particularly, the disassembly of the operating fluidpath 6 is not preferable. On the other hand, in FIG. 7, not theevaporator 4 or the heater 31 but the second heat source fluid heater 21is disassembled and cleaned, and therefore, it is not necessary todisassemble the operating fluid path 6.

As described above, the power generating system in the presentembodiment heats the water of the first temperature by using the secondheat source fluid to produce the water of the second temperature to beused as the hot water. Therefore, according to the present embodiment,it is possible to improve the energy utilization rate in the powergenerating system.

The heat source fluid heater 21, the heat source fluid pump 22, the heatsource fluid path 23 and the heater 31 in the present embodiment may beapplied to any of the second to sixth embodiments. This is true of theheat source fluid heater 21, the heat source fluid pump 22, the heatsource fluid path 23 and the heater 31 in the eighth to tenthembodiments to be described later.

In addition, the second heat source fluid in the present embodiment isheated by the heat of the first heat source fluid, not through the otherheat source fluid, but may be heated through one or more kinds of thirdheat source fluids by the heat of the first heat source fluid. That is,the second heat source fluid in the present embodiment may be directlyor indirectly heated by the heat of the first heat source fluid. This istrue of the eighth to tenth embodiments to be described later.

In addition, the first heat source fluid in the present embodiment isheated by the heat of the low-temperature heat source such as biomassfuel, not through the other heat source fluid, but may be heated throughone or more kinds of fourth heat source fluids by the heat of thelow-temperature heat source. That is, the first heat source fluid in thepresent embodiment may be directly or indirectly heated by the heat ofthe low-temperature heat source. This is true of the eighth to tenthembodiments to be described later.

Further, the configuration of the present embodiment can be effectivelyapplied in a case where the maximum temperature of the second heatsource fluid in the second heat source fluid path 23 is, for example,200° C. or less.

Eighth Embodiment

FIG. 8 is a schematic diagram showing the configuration of a powergenerating system according to an eighth embodiment. In FIG. 8,components identical or similar to those in FIG. 7 are referred to asidentical signs, and an explanation overlapping the explanation in FIG.7 is omitted. This is true of the ninth and tenth embodiments.

In the present embodiment, the heater 31 is provided in the first heatsource fluid path 3. The heater 31 heats the water from the water path34 by using the first heat source fluid to produce water to be used ashot water. The hot water is conveyed through the water path 34 and isreserved in the hot water tank 32. The heater 31 in the presentembodiment heats the water by using the first heat source fluid flowingdownstream of the second heat source fluid heater 21. The first heatsource fluid discharged from the second heat source fluid heater 21flows into the heater 31, and is lowered in temperature by heating thewater in the heater 31. The first heat source fluid circulates among thefirst heat source fluid heater 1, the second heat source fluid heater 21and the heater 31 through the first heat source fluid path 3.

In many cases, a temperature of the first heat source fluid in the inletof the heater 31 in the eighth embodiment is higher than a temperatureof the second heat source fluid in the inlet of the heater 31 in theseventh embodiment. Therefore, according to the eighth embodiment, thewater tends to be easily heated to a higher temperature. In addition,according to the eighth embodiment, it is not necessary to disassembleand clean the water path 34. On the other hand, according to the seventhembodiment, it is possible to use the higher percentage of thermalenergy for the power generation by the power generator 8.

Ninth Embodiment

FIG. 9 is a schematic diagram showing the configuration of a powergenerating system according to a ninth embodiment.

The heater 31 in the eighth embodiment, as shown in FIG. 8, heats thewater by using the first heat source fluid flowing downstream of thesecond heat source fluid heater 21. On the other hand, the heater 31 inthe ninth embodiment, as shown in FIG. 9, heats the water by using thefirst heat source fluid flowing upstream of the second heat source fluidheater 21.

In the present embodiment, a temperature of the first heat source fluidin the inlet of the heater 31 is higher than a temperature of the firstheat source fluid in the inlet of the second heat source fluid heater21. Therefore, according to the present embodiment, the water tends tobe easily heated to a higher temperature. On the other hand, accordingto the eighth embodiment, it is possible to use the higher percentage ofthe thermal energy for the power generation by the power generator 8.

FIG. 10 is a schematic diagram showing the configuration of a powergenerating system according to a modification of the ninth embodiment.

The heater 31 in the seventh embodiment, as shown in FIG. 7, heats thewater by using the second heat source fluid flowing downstream of theevaporator 4. On the other hand, the heater 31 in the presentmodification, as shown in FIG. 10, heats the water by using the secondheat source fluid flowing upstream of the evaporator 4.

In the present modification, a temperature of the second heat sourcefluid in the inlet of the heater 31 is higher than a temperature of thesecond heat source fluid in the inlet of the evaporator 4. Therefore,according to the present modification, the water tends to be easilyheated to a higher temperature. In addition, according to the presentmodification, it is not necessary to disassemble and clean the waterpath 34. On the other hand, according to the seventh embodiment, it ispossible to use the higher percentage of the thermal energy for thepower generation by the power generator 8.

Tenth Embodiment

FIG. 11 is a schematic diagram showing the configuration of a powergenerating system according to a tenth embodiment.

The power generating system in FIG. 11 includes first and second heaters31 a, 31 b instead of the heater 31. The first heater 31 a is providedin the first heat source fluid path 3. The second heater 31 b isprovided in the second heat source fluid path 23. The first and secondheaters 31 a, 31 b heat the water of the first temperature to producethe water of the second temperature to be used as hot water.

The first heat source fluid is conveyed through the first heat sourcefluid path 3 by the first heat source fluid pump 2, and is heated by thefirst heat source fluid heater 1. The first heat source fluid dischargedfrom the first heat source fluid heater 1 flows into the second heatsource fluid heater 21, and is lowered in temperature by heating thesecond heat source fluid in the second heat source fluid heater 21.

The second heat source fluid is conveyed through the second heat sourcefluid path 23 by the second heat source fluid pump 22, and is heated bythe second heat source fluid heater 21. The second heat source fluiddischarged from the second heat source fluid heater 21 flows into theevaporator 4, and is lowered in temperature by heating the operatingfluid in the evaporator 4.

The operating fluid of the liquid is conveyed through the operatingfluid path 6 by the operating fluid pump 5, is heated by the evaporator4, and is converted in phase into the operating fluid of the gas. Anexample of the operating fluid is a low-boiling medium of CFC or thelike. The operating fluid discharged from the evaporator 4 flows intothe expansion module 7 and expands in the expansion module 7 to drivethe rotational shaft of the expansion module 7. The rotational shaft ofthe expansion module 7 is connected to the power generator 8, and thepower generator 8 generates power by using shaft power of the rotationalshaft. The operating fluid is lowered in pressure and temperature in theexpansion module 7, is discharged from the expansion module 7 and flowsinto the condenser 9. The operating fluid having flowed into thecondenser 9 is cooled by water in the condenser 9 to be converted inphase into the operating fluid of the liquid.

The water is conveyed through the water path 34 by the water pump 33 andis heated by condensation heat of the operating fluid in the condenser9. The water discharged from the condenser 9 is conveyed through thewater path 34, and is supplied to the second heater 31 b. A temperatureof the water in the inlet of the condenser 9 is, for example, 15° C. Atemperature of the water in the outlet of the condenser 9 is, forexample, 30° C. 30° C. is an example of the first temperature.

The second heater 31 b heats the water from the water path 34 by usingthe second heat source fluid. The water heated by the second heater 31 bis conveyed through the water path 34, and is supplied to the firstheater 31 a. The first heater 31 a heats the water flowing downstream ofthe second heater 31 b by using the first heat source fluid, andproduces the water to be used as the hot water. A temperature of the hotwater is, for example, 60° C. 60° C. is an example of the secondtemperature. The hot water is conveyed through the water path 34, and isreserved in the hot water tank 32.

The first heater 31 a in the present embodiment heats the water by usingthe first heat source fluid flowing downstream of the second heat sourcefluid heater 21. The first heat source fluid discharged from the secondheat source fluid heater 21 flows into the first heater 31 a, and islowered in temperature by heating the water in the first heater 31 a.The first heat source fluid circulates among the first heat source fluidheater 1, the second heat source fluid heater 21 and the first heater 31a through the first heat source fluid path 3.

In addition, the second heater 31 b in the present embodiment heats thewater by using the second heat source fluid flowing downstream of theevaporator 4. The second heat source fluid discharged from theevaporator 4 flows into the second heater 31 b, and is lowered intemperature by heating the water in the second heater 31 b. The secondheat source fluid circulates among the second heat source fluid heater21, the evaporator 4 and the second heater 31 b through the second heatsource fluid path 23.

In the present embodiment, the first heater 31 a is heated by the secondheater 31 b to heat the water flowing out of the second heater 31 b, butin the flowing order, the second heater 31 b may be heated by the firstheater 31 a and may heat the water flowing out of the first heater 31 a.In a case where a temperature of the first heat source fluid in theoutlet of the first heater 31 a is lower than a temperature of thesecond heat source fluid in the inlet of the second heater 31 b, it ispreferable to arrange the first heater 31 a downstream of the secondheater 31 b. In addition, in the present embodiment, the first heater 31a and the second heater 31 b are arranged in series to the flow of thewater, but may be arranged in parallel to the flow of the water.

FIG. 12 is a schematic diagram showing the configuration of a powergenerating system according to a modification of the tenth embodiment.

The first heater 31 a of the tenth embodiment, as shown in FIG. 11,heats the water by using the first heat source fluid flowing downstreamof the second heat source fluid heater 21. On the other hand, the firstheater 31 a of the present modification, as shown in FIG. 12, heats thewater by using the first heat source fluid flowing upstream of thesecond heat source fluid heater 21.

In addition, the second heater 31 b of the tenth embodiment, as shown inFIG. 11, heats the water by using the second heat source fluid flowingdownstream of the evaporator 4. On the other hand, the first heater 31 aof the present modification, as shown in FIG. 12, heats the water byusing the second heat source fluid flowing upstream of the evaporator 4.

In this manner, the first heater 31 a may be arranged downstream orupstream of the second heat source fluid heater 21. Likewise, the secondheater 31 b may be arranged downstream or upstream of the evaporator 4.In addition, one of the first and second heaters 31 a, 31 b may bearranged as shown in FIG. 11, and the other of the first and secondheaters 31 a, 31 b may be arranged as shown in FIG. 12.

In the present modification, the first heater 31 a heats the waterflowing downstream of the second heater 31 b, but the second heater 31 bmay heat the water flowing downstream of the first heater 31 a. Further,in the present modification, the first and second heaters 31 a, 31 b arearranged in series to the flow of the water, but the first and secondheaters 31 a, 31 b may be arranged in parallel to the flow of the water.

As described above, the power generating system of the presentembodiment includes the first and second heaters 31 a, 31 b instead ofthe heater 31. In a case of adopting this configuration, the heatexchangers in the power generating system increase in number, but thepower generating system can be designed such that a difference intemperature between the heating fluid and the heated fluid is madesmall. Specifically, the power generating system can be designed suchthat a difference in temperature between the first heat source fluid andthe second heat source fluid or a difference in temperature between thesecond heat source fluid and the operating fluid is made small. As aresult, according to the present embodiment, the water tends to beeasily heated to a higher temperature.

In addition, the first and second heaters 31 a, 31 b in FIGS. 11 and 12may produce steam instead of producing the water to be used as the hotwater. That is, the first and second heaters 31 a, 31 b may producewater of a gas instead of producing the water of the liquid. In thiscase, the hot water tank 32 is replaced by, for example, a facility forreserving, conveying or using the steam. This is true of third andfourth heaters 31 c, 31 d in twelfth, fourteenth, sixteenth, eighteenth,twentieth, twenty-first and twenty-second embodiments (however, in thetwentieth embodiment, the heat use destination 37 is replaced by, forexample, the facility for reserving, conveying or using the steam).

Eleventh Embodiment

FIG. 13 is a schematic diagram showing the configuration of a powergenerating system according to an eleventh embodiment.

When FIG. 1 and FIG. 13 are compared, the power generating system inFIG. 13 does not include the heat source fluid heater 1, the heat sourcefluid pump 2, the heat source fluid path 3, the evaporator 4 and theoperating fluid pump 5 shown in FIG. 1. An example of the operatingfluid flowing in the operating fluid path 6 in FIG. 13 is a gas ofgeothermal steam or the like.

The operating fluid path 6 in FIG. 13 is branched into a first fluidpath 61 provided with the expansion module 7 and the condenser 9 and asecond fluid path 62 provided with the heater 31. The first fluid path61 and the second fluid path 62 are branched from a single flow path L₂in a fifth point P₅. The operating fluid of the gas flowing in theoperating fluid path 6 is branched in the fifth point P₅ and flows intothe first fluid path 61 and the second fluid path 62.

The operating fluid having flowed in the first fluid path 61 isintroduced in the expansion module 7 to drive the rotational shaft ofthe expansion module 7. The power generator 8 generates power by usingthe shaft power of the rotational shaft. The operating fluid isthereafter discharged into the first fluid path 61 from the expansionmodule 7, and flows into the condenser 9. The operating fluid havingflowed into the condenser 9 is cooled by water (cooling water) from thewater path 34 to be converted into the operating fluid of the liquid andbe returned back to the ground.

On the other hand, the operating fluid having flowed in the second fluidpath 62 is introduced in the heater 31. The heater 31 heats the waterfrom the water path 34 by using the operating fluid in the second fluidpath 62 to produce the water to be used as the hot water. The hot wateris conveyed through the water path 34 to be reserved in the hot watertank 32. On the other hand, the operating fluid in the second fluid path62 is lowered in temperature by heating the water in the heater 31 to bethe condensed fluid, and is returned back to the ground. The operatingfluid all may be condensed, only a part thereof may be condensed or theoperating fluid may not be condensed at all (this is true of thirteenth,fifteenth and seventeenth embodiments, which will be described later).

The operating fluid in the first fluid path 61 is introduced in theexpansion module 7 and is used as the operating fluid, but the operatingfluid in the second fluid path 62 is not used as the operating fluid.However, since the operating fluid in the second fluid path 62 is thesame as the operating fluid in the first fluid path 61, in the presentembodiment the operating fluid in the second fluid path 62 is describedas the operating fluid as similar to the operating fluid in the firstfluid path 61. This is true of the subsequent embodiments.

According to the present embodiment, the heater 31 can be applied alsoto the power generating system not provided with the evaporator 4. Theconfiguration of the present embodiment is effective since a ratio ofthe condensed heat to the power generation amount becomes large when themaximum temperature of the operating fluid in the operating fluid path 6is 200° C. or less.

Twelfth Embodiment

FIG. 14 is a schematic diagram showing the configuration of a powergenerating system according to a twelfth embodiment.

In FIG. 14, the heater 31 in FIG. 13 is replaced by the third and fourthheaters 31 c, 31 d. The third heater 31 c is provided in the secondfluid path 62. The fourth heater 31 d is provided downstream of thethird heater 31 c in the second fluid path 62.

In addition, the water path 34 in FIG. 14 is branched into a first waterpath 63 provided with the condenser 9 and a second water path 64provided with the fourth heater 31 d. The first and second water paths63, 64 are branched from a single flow path L₃ in a sixth point P₆ andmerge into the single flow path L₃ in a seventh point P₇. The waterflowing in the water path 34 is branched into the first and second waterpaths 63, 64 in the sixth point P₆, and merges from the first and secondwater paths 63, 64 in the seventh point P₇. The third heater 31 c isprovided in the flow path L₃ (third water path) after the merging.

The operating fluid having flowed into the first fluid path isintroduced in the expansion module 7 to drive the rotational shaft ofthe expansion module 7. The power generator 8 generates power by usingthe shaft power of the rotational shaft. The operating fluid isthereafter discharged into the first fluid path 61 from the expansionmodule 7, and flows into the condenser 9. The operating fluid havingflowed into the condenser 9 is cooled by water (cooling water) from thefirst water path 63 to be converted into the operating fluid of theliquid and be returned back to the ground.

On the other hand, the operating fluid having flowed in the second fluidpath 62 is introduced in the third heater 31 c, and next, in the fourthheater 31 d. The fourth heater 31 d heats the water from the secondwater path 64 by using the operating fluid in the second fluid path 62.The water discharged from the condenser 9 to the first water path 63 andthe water discharged from the fourth heater 31 d to the second waterpath 64 merge in the seventh point P₇, which is introduced in the thirdheater 31 c. The third heater 31 c heats the water by using theoperating fluid in the second fluid path 62 to produce the water to beused as the hot water. The hot water is conveyed through the water path34 to be reserved in the hot water tank 32. On the other hand, theoperating fluid in the second fluid path 62 is lowered in temperature byheating the water in the third and fourth heaters 31 c, 31 d to be thecondensed fluid, which is returned back to the ground. The operatingfluid all may be condensed, only a part thereof may be condensed or theoperating fluid may not be condensed at all (this is true of fourteenth,sixteenth, eighteenth, twenty-third and twenty-fourth embodiments, whichwill be described later).

In the eleventh embodiment, in some cases the temperature of theoperating fluid discharged from the heater is higher than that of thewater discharged from the condenser 9. In this case, it is possible tofurther collect the heat of the potential heat amount of the operatingfluid. On the other hand, in the present embodiment the third heater 31c collects the heat of the potential heat amount of the operating fluidby water and the fourth heater 31 d collects heat of the potential heatamount of the operating fluid by lower-temperature water. Therefore,according to the present embodiment, it is possible to sufficientlycollect the heat of the potential heat amount of the operating fluid.

Thirteenth Embodiment

FIG. 15 is a schematic diagram showing the configuration of a powergenerating system according to a thirteenth embodiment.

When FIGS. 1 and 15 are compared, the power generating system in FIG. 15does not include the heat source fluid heater 1, the heat source fluidpump 2 and the heat source fluid path 3 shown in FIG. 1. An example ofthe evaporator 4 in FIG. 15 includes a small-sized biomass boiler forburning biomass fuel, a solar energy collector for collecting solarenergy, and an exhaust heat collector for collecting factory exhaustheat or the like. An example of the operating fluid is water of a gas orliquid.

The operating fluid path 6 in FIG. 15 is branched into the first fluidpath 61 provided with the expansion module 7 and the condenser 9 and thesecond fluid path 62 provided with the heater 31. The first fluid path61 and the second fluid path 62 are branched from the single flow pathL₂ in the fifth point P₅ and merge into the single flow path L₂ in aneighteenth point P₈. The operating fluid flowing in the operating fluidpath 6 is branched into the first and second fluid paths 61, 62 in thefifth point P₅, and merges from the first fluid path 61 and the secondfluid path 62 in the eighth point P_(g). The evaporator 4 and theoperating fluid pump 5 are provided in the flow path L₂ (third fluidpath 66) after the merging. In addition, the first fluid path 61 isprovided with an operating fluid pump 65.

The operating fluid of the liquid is conveyed through the operatingfluid path 6 by the operating fluid pump 5 and is heated by theevaporator 4 to be converted into the operating fluid of a gas. Theoperating fluid of the gas discharged from the evaporator 4 is branchedin the fifth point P₅, and flows into the first fluid path 61 and thesecond fluid path 62.

The operating fluid having flowed into the first fluid path 61 isintroduced in the expansion module 7 to drive the rotational shaft ofthe expansion module 7. The power generator 8 generates power by usingthe shaft power of the rotational shaft. The operating fluid isthereafter discharged into the first fluid path 61 from the expansionmodule 7, and flows into the condenser 9. The operating fluid havingflowed into the condenser 9 is cooled by water (cooling water) from thewater path 34 to be converted into the operating fluid of the liquid andis conveyed to the eighth point P₈ by the operating fluid pump 65.

On the other hand, the operating fluid having flowed in the second fluidpath 62 is introduced in the heater 31. The heater 31 heats the waterfrom the water path 34 by using the operating fluid in the second fluidpath 62 to produce the water used as the hot water. The hot water isconveyed through the water path 34 to be reserved in the hot water tank32. On the other hand, the operating fluid in the second fluid path 62is lowered in temperature to be the condensed fluid by heating the waterin the heater 31, and is discharged to the eighth point P₈.

The operating fluid discharged from the condenser 9 to the first fluidpath 61 and the operating fluid discharged from the heater 31 to thesecond fluid path 62 merge in the eighth point P₈ to be introduced inthe evaporator 4. Thus, the operating fluid circulates among theevaporator 4, the expansion module 7, the condenser 9 and the heater 31through the operating fluid path 6. The operating fluid pump 65 isprovided as needed such that a pressure of the operating fluid flowingfrom the first fluid path 61 into the eighth point P₈ is made equal toor closer to a pressure of the operating fluid flowing from the secondfluid path 62 into the eighth point P₈.

According to the present embodiment, the heater 31 can be applied alsoto the power generating system not provided with the heat source fluidheater 1. The present embodiment is applicable even if the heat sourcein the evaporator 4 is a high-temperature heat source, but iseffectively applicable in a case where the heat source in the evaporator4 is a low-temperature heat source such as biomass fuel, solar energy,factory exhaust heat or hot spring heat. This is true of fourteenth,seventeenth and eighteenth embodiments to be described later. The reasonis that in a case where the heat source in the evaporator 4 is alow-temperature heat source, the power generation coefficient is lower,and the energy utilization rate in a case of not applying the presentembodiment is low.

The configuration of the present embodiment is effectively applicablewhen the maximum temperature of the heat source fluid in the operatingfluid path 6 is, for example, 200° C. or less.

Fourteenth Embodiment

FIG. 16 is a schematic diagram showing the configuration of a powergenerating system according to a fourteenth embodiment.

In FIG. 16, the heater 31 in FIG. 15 is replaced by the third and fourthheaters 31 c, 31 d. In addition, the water path 34 in FIG. 16 isbranched into a first water path 63 provided with the condenser 9 and asecond water path 64 provided with the fourth heater 31 d. The aboveconfiguration is the same as the configuration shown in FIG. 14.

In the thirteenth embodiment, in some cases the temperature of theoperating fluid discharged from the heater is higher than that of thewater discharged from the condenser 9. In this case, it is possible tofurther collect heat of the potential heat amount of the operatingfluid. On the other hand, in the present embodiment the third heater 31c collects the heat of the potential heat amount of the operating fluidby water, and the fourth heater 31 d collects the heat of the potentialheat amount of the operating fluid by low-temperature water. Therefore,according to the present embodiment, it is possible to sufficientlycollect the heat of the potential heat amount of the operating fluid.

Fifteenth Embodiment

FIG. 17 is a schematic diagram showing the configuration of a powergenerating system according to a fifteenth embodiment.

The operating fluid path 6 in FIG. 13 is branched into the first fluidpath 61 provided with the expansion module 7 and the condenser 9 and thesecond fluid path 62 provided with the heater 31. On the other hand, theoperating fluid path 6 in FIG. 17 includes a fourth fluid path 67 thatconveys the operating fluid discharged from an exhaust port 7 a of theexpansion module 7, and is provided with the condenser 9 and a fifthfluid path 68 that conveys the operating fluid extracted from anextraction port 7 b of the expansion module 7 and is provided with theheater 31. The extraction port 7 b of the expansion module 7 is providedin a preceding stage of the exhaust port 7 a of the expansion module 7.

The configuration and function of the fourth and fifth fluid paths 67,68 in FIG. 17 are the same as those of the first and second fluid paths61, 62 in FIG. 13. Accordingly, the water discharged from the condenser9 is heated by the operating fluid in the heater 31 to produce the hotwater. According to the present embodiment, the heater 31 can be appliedalso to the power generating system not provided with the evaporator 4.

A temperature and a pressure of the operating steam in the extractionport 7 b of the expansion module 7 are lower than a temperature and apressure of the operating steam in the inlet of the expansion module 7.According to the present embodiment, it is possible to change thetemperature and pressure of the operating steam for the heater 31 bychanging a position of the extraction port 7 b. In addition, accordingto the present embodiment, it is possible to use more energy of theoperating fluid for power generation as compared to the eleventhembodiment. On the other hand, according to the eleventh embodiment, itis possible to adopt the heater 31 without providing the expansionmodule 7 with the extraction port 7 b. This is true of theaforementioned twelfth to fourteenth embodiments and after-mentionedsixteenth to twenty-second embodiments.

Sixteenth Embodiment

FIG. 18 is a schematic diagram showing the configuration of a powergenerating system according to a sixteenth embodiment.

In FIG. 18, the first and second fluid paths 61, 62 in FIG. 14 arereplaced by the fourth and fifth fluid paths 67, 68. Therefore, thecondenser 9 is provided in the fourth fluid path 67, and the third andfourth heaters 31 c, 31 d are provided in the fifth fluid path 68.

According to the present embodiment, it is possible to sufficientlycollect heat of the potential heat amount of the operating fluid by thethird and fourth heaters 31 c, 31 d.

Seventeenth Embodiment

FIG. 19 is a schematic diagram showing the configuration of a powergenerating system according to a seventeenth embodiment.

In FIG. 19, the first and second fluid paths 61, 62 in FIG. 15 arereplaced by the fourth and fifth fluid paths 67, 68. Therefore, thecondenser 9 is provided in the fourth fluid path 67, and the heater 31is provided in the fifth fluid path 68. Further, the fourth and fifthfluid paths 67, 68 merge into the single flow path L₂ in the eighthpoint P₈. The evaporator 4 and the operating fluid pump 5 are providedin the flow path L₂ (sixth fluid path 69) after the merging. Inaddition, the fourth fluid path 67 is provided with the operating fluidpump 65.

According to the present embodiment, the heater 31 can be applied evento the power generating system not provided with the heat source fluidheater 1.

Eighteenth Embodiment

FIG. 20 is a schematic diagram showing the configuration of a powergenerating system according to an eighteenth embodiment.

In FIG. 20, the first and second fluid paths 61, 62 in FIG. 16 arereplaced by the fourth and fifth fluid paths 67, 68. Therefore, thecondenser 9 is provided in the fourth fluid path 67, and the third andfourth heaters 31 c, 31 d are provided in the fifth fluid path 68.Further, the fourth and fifth fluid paths 67, 68 merge into the singleflow path L₂ in the eighth point P₈. The evaporator 4 and the operatingfluid pump 5 are provided in the flow path L₂ (sixth fluid path 69)after the merging. In addition, the fourth fluid path 67 is providedwith the operating fluid pump 65.

According to the present embodiment, it is possible to sufficientlycollect heat of the potential heat amount of the operating fluid by thethird and fourth heaters 31 c, 31 d.

Nineteenth Embodiment

FIG. 21 is a schematic diagram showing the configuration of a powergenerating system according to a nineteenth embodiment.

The operating fluid path 6 in FIG. 13 is branched into the first andsecond fluid paths 61, 62. The first fluid path 61 is provided with theexpansion module 7 and the condenser 9, and the second fluid path 62 isprovided with the heater 31. On the other hand, the heater 31 in FIG. 21is provided upstream of the expansion module 7 in the operating fluidpath 6 with no branch. The heater 31 in FIG. 21 heats the water in thewater path 34 by using the operating fluid upstream of the expansionmodule 7, and discharges the operating fluid to the expansion module 7.

In the eleventh embodiment, in some cases the temperature of theoperating fluid discharged from the heater is higher than that of thewater discharged from the condenser 9. In this case, it is possible tofurther collect the heat of the potential heat amount of the operatingfluid. On the other hand, in the present embodiment, after the heater 31collects the heat of the potential heat amount of the operating fluid bya desired amount, the operating fluid is used in the expansion module 7,which is discharged to the condenser 9. Therefore, according to thepresent embodiment, it is possible to sufficiently collect the heat ofthe potential heat amount of the operating fluid.

The arrangement of the heater 31 in the present embodiment can beapplied not only to the eleventh embodiment but also to the thirteenth,twentieth and twenty-first embodiments.

Twentieth Embodiment

FIG. 22 is a schematic diagram showing the configuration of a powergenerating system according to a twentieth embodiment.

In FIG. 22, the hot water tank 32 in FIG. 14 is replaced by the heat usedestination 37, and the water path 34 in FIG. 14 is replaced by thecirculation water path 38. The details of the heat use destination 37and the circulation water path 38 are similar to those in FIG. 4.

For example, the operating fluid instead of the hot water (or steam) canbe supplied to the heat use destination 37. However, in a case where theoperating fluid is geothermal steam, in many cases the operating fluidcontains corrosiveness components or earth and sand. In this case, it isnecessary to take measures of removing the corrosiveness components orearth and sand from the operating fluid. On the other hand, according tothe present embodiment, it is possible to make this measure unnecessaryby supplying clean hot water (or steam) instead of the operating fluidto the heat use destination 37.

According to the present embodiment, as similar to the fourthembodiment, it is possible to repeatedly use the hot water (or steam).The heat use destination 37 and the circulation water path 38 of thepresent embodiment can be applied not only to the twelfth embodiment butalso to the eleventh, thirteenth to nineteenth, twenty-first andtwenty-second embodiments.

Twenty-first Embodiment

FIG. 23 is a schematic diagram showing the configuration of a powergenerating system according to a twenty-first embodiment.

The power generating system in FIG. 23 includes the components shown inFIG. 14, and besides, valves 71 to 76. The valve 71 is provided upstreamof the expansion module 7 in the first fluid path 61. The valve 72 isprovided upstream of the third heater 31 c in the second fluid path 62.The valve 73 is provided upstream of the condenser 9 in the first waterpath 63. The valve 74 is provided upstream of the fourth heater 31 d inthe second water path 64. The valve 75 is provided downstream of thecondenser 9 in the first fluid path 61. The valve 76 is provideddownstream of the fourth heater 31 d in the second fluid path 62.

In a case of performing only the power generation in the powergenerating system, the valves 71, 73, 75 are opened, and the valve 72 isclosed. On this occasion, it is preferable to close the valve 74, butthe valve 76 may be opened or closed. In this case, since the water ofthe water path 34 is heated only by the condenser 9, the water becomes alow-temperature hot water. In addition, it is possible to adjust a powergeneration amount of the power generator 8 by adjusting an openingdegree of the valve 71, and it is possible to adjust a flow amount ofthe water in the water path 34 by adjusting an opening degree of thevalve 73.

In a case of performing only the hot water production in the powergenerating system, the valves 72, 74, 76 are opened, and the valve 71 isclosed. On this occasion, it is preferable to close the valve 73, butthe valve 75 may be opened or closed. In this case, it is possible toadjust a flow amount of the water (that is, a hot water flow amount) inthe water path 34 by adjusting an opening degree of the valve 74, and itis possible to adjust a temperature or a heat amount of the hot water byadjusting an opening degree of the valve 72.

In a case of performing both of the power generation and the hot waterproduction in the power generating system, all of the valves 71 to 76are opened. In this case, it is possible to adjust a power generationamount of the power generator 8, and a flow amount, a temperature and aheat amount of the hot water by adjusting an opening degree of each ofthe valves 71 to 74.

In the present embodiment, the valves 74 to 76 may be not installed, butit is preferable to install them for the flow path management.

As described above, according to the present embodiment, it is possibleto select three kinds of operations in the power generating system bythe valves 71 to 76. That is, it is possible to select performing onlythe power generation, performing only the hot water production or bothof the power generation and the hot water production. In addition,according to the present embodiment, it is possible to adjust a powergeneration amount of the power generator 8, and a flow amount, atemperature and a heat amount of the hot water.

The valves 71 to 76 in the present embodiment can be applied not only tothe twelfth embodiment but also to the eleventh, thirteenth, fourteenthand twentieth embodiments.

Twenty-second Embodiment

FIG. 24 is a schematic diagram showing the configuration of a powergenerating system according to a twenty-second embodiment.

The power generating system in FIG. 24 includes the components shown inFIG. 18, and besides, the valves 73, 74 and valves 77, 78. The valve 73is, as described above, provided upstream of the condenser 9 in thefirst water path 63. The valve 74 is, as described above, providedupstream of the fourth heater 31 d in the second water path 64. Thevalve 77 is provided upstream of the third heater 31 c in the fifthfluid path 68. The valve 78 is provided downstream of the fourth heater31 d in the fifth fluid path 68.

In a case of performing only the power generation in the powergenerating system, the valve 73 is opened, and the valves 77, 78 areclosed. At this time, it is preferable to close the valve 74. In thiscase, since the water of the water path 34 is heated only by thecondenser 9, the water becomes a low-temperature hot water.

In a case of performing both of the power generation and the hot waterproduction in the power generating system, the valves 73, 77, 78 areopened, and the valve 74 is closed in a case of not placing importanceon the hot water production. In this case, the water in the water path34 is heated only by the condenser 9 and the third heater 31 c.

In a case of performing both of the power generation and the hot waterproduction in the power generating system, the valves 73, 74, 77, 78 allare opened in a case of placing importance on the hot water production.In this case, the water in the water path 34 is heated by the condenser9, the third heater 31 c and the fourth heater 31 d.

In the present embodiment, the valves 73, 74, 78 may be not installed,but it is preferable to install them for the flow path management.

As described above, according to the present embodiment, it is possibleto select three kinds of operations in the power generating system bythe valves 73, 74, 77, 78. In addition, according to the presentembodiment, it is possible to adjust a power generation amount of thepower generator 8, and a flow amount, a temperature and a heat amount ofthe hot water by these valves.

The valves 73, 74, 77, 78 in the present embodiment can be applied notonly to the sixteenth embodiment but also to the fifteenth, seventeenthand eighteenth embodiments.

Twenty-third Embodiment

FIG. 25 is a schematic diagram showing the configuration of a coolingsystem according to a twenty-third embodiment.

The cooling system in FIG. 25, as similar to the cooling system in FIG.42, includes the heat source fluid heater 1, the heat source fluid pump2, the heat source fluid path 3, the refrigerator 16, the cooled fluidpump 17, the cooled fluid path 18 and the cold load 19. The refrigerator16 includes the heat absorbing module 16 a, the cooling module 16 b andthe heat releasing module 16 c. The refrigerator 16 in the presentembodiment is of an absorption type or adsorption type, and, forexample, has the structure shown in FIG. 46 or the structure shown inFIGS. 47 and 48. The cooling system in FIG. 25 further includes theheater 31, the hot water tank 32, the water pump 33 and the water path34, configuring the exhaust heat collecting system for collecting theexhaust heat of the refrigerator 16 and the like.

The heat source fluid (first heat source fluid) is heated by the heatsource fluid heater 1 to heat the heat absorbing module 16 a and belowered in temperature. The heat source fluid in the present embodiment,as shown in FIG. 45, may be made as the hot spring water from the ground10. This is true of twenty-fourth to thirty-second embodiments to bedescribed later.

The refrigerator 16 includes the heat absorbing module 16 a, the coolingmodule 16 b and the heat releasing module 16 c, and the cooling mediumis contained in the refrigerator 16. An example of the cooling medium isammonia in case where the refrigerator 16 is of an absorption type, andis water in case where the refrigerator 16 is of an adsorption type. Thecooling module 16 b cools the cooled fluid by evaporation heat of thecooling medium. An example of the cooled fluid is water. In case wherethe refrigerator 16 is of an absorption type, the heat absorbing module16 a heats the absorption liquid having absorbed the cooling medium bythe heat source fluid to vaporize the cooling medium. The heat releasingmodule 16 c cools the cooling medium vaporized from the absorptionliquid by the cooling water to liquidize the cooling medium. On theother hand, in a case where the refrigerator 16 is of an adsorptiontype, the heat absorbing module 16 a heats the adsorption agent havingadsorbed the cooling medium by the heat source fluid to cause thecooling medium to be desorbed from the adsorption agent. The heatreleasing module 16 c cools the adsorption agent by the cooling water tocause the adsorption agent to adsorb the cooling medium. The coolingmodule 16 b cools the cooled fluid by using the cooling medium from theheat releasing module 16 c.

The cooled fluid is conveyed through the cooled fluid path 18 by thecooled fluid pump 17, and is cooled by the cooling module 16 b. Thecooled fluid discharged from the cooling module 16 b flows into the coldload 19, and is increased in temperature by cooling the cold load 19. Anexample of the cold load 19 is cooling target facilities such asbuilding cooling or cooling target devices such as server computers.

The cooling water is increased in temperature by cooling the heatreleasing module 16 c, and is supplied to the heater 31 through thewater path 34. The heater 31 is provided in the heat source fluid path3. The heater 31 heats the water from the water path 34 by using theheat source fluid in the heat source fluid path 3 to produce the waterused as the hot water. The hot water is conveyed through the water path34 and is reserved in the hot water tank 32. The heat source fluiddischarged from the heat absorbing module 16 a is lowered in temperatureby heating the water in the heater 31.

In the present embodiment, the heat discharged in the heat releasingmodule 16 c is given to the water before being heated by the heater 31without being given to the cooling tower 13. An example of the waterincludes tap water. In addition, a temperature of the reserved hot wateris made to, for example, 60° C. estimated as a generally usable hotwater temperature. This hot water is effectively used in bathingfacilities, for dish washing in restaurants or the like. In the presentembodiment, since there is no heat put aside externally, the energyutilization rate improves to 100%. The energy use rate in the presentembodiment is a ratio between thermal energy given to the heat sourcefluid by the heat source fluid heater 1 and energy used by the coolingsystem.

Here, a temperature of water in the water pump 33 is set to 15° C., atemperature of water heated by the heat releasing module 16 c is set to30° C., and a temperature of water heated by the heater 31 is set to 60°C. 30° C. is an example of the first temperature, and 60° C. is anexample of the second temperature. The refrigerator 16 is of anadsorption type, and COP of the refrigerator 16 is assumed to be 0.5 asa typical value.

In this case, when the drive heat E2 of the refrigerator 16 is assumedto be “2”, since an absolute value E1 of the cold heat becomes “1”, theexhaust heat E3 of the refrigerator 16 in the conventional coolingsystem becomes “3”. However, in the present embodiment, since use hotheat E4 of the refrigerator 16 becomes “3” because of using this heatfor hot water production. Further, in the present embodiment, the driveheat of the heater 31 becomes “6” and the use hot heat of the heater 31becomes “6” because of using the heat as much as twice for hot waterproduction in the heater 31. As a result, the drive heat (drive heat ofthe refrigerator 16 and the heater 31) E2′ of the cooling system becomes“8”, and the use hot heat (use hot heat of the refrigerator 16 and theheater 31) E4′ of the cooling system becomes “9”. As a result, when ause heat conversion rate of the cooling system is assumed to be(E1+E4′)/E2′ and an exhaust heat rate of the cooling system is assumedto be E3/E2′, the use heat conversion rate of the present embodimentbecomes 1.25 (=10/8), and the exhaust heat rate of the presentembodiment becomes 0 (=0/8).

FIG. 50 is a supplementary diagram explaining the cooling systemaccording to the twenty-third embodiment.

The cooling system in FIG. 50 includes the components shown in FIG. 25,and besides, the cooling water pump 11, the cooling water path 12, thecooling tower 13, the blower 14 and the atmosphere introducing portion15.

In FIG. 50, the water in the water path 34 is heated only by the heater31, and is not heated in the heat releasing module 16 c. The heatdischarged in the heat releasing module 16 c is put aside externally. Inthis case, in the above-mentioned numerical example, the use heatconversion rate of the cooling system becomes 0.875 (=7/8), and theexhaust heat rate of the cooling system becomes 0.375 (=3/8).

In the cooling system in FIG. 42 or 44, the use heat conversion rate ofthe cooling system becomes 0.5 (=1/2), and the exhaust heat rate of thecooling system becomes 1.5 (=3/2).

As described above, the cooling system according to the presentembodiment uses the heat source fluid from the heat source fluid path 3to heat the water of the first temperature and produce the water of thesecond temperature to be used as the hot water. Therefore, according tothe present embodiment, it is possible to effectively use the exhaustheat in the cooling system.

The present embodiment is applicable even if the heat source in the heatsource fluid heater 1 is a high-temperature heat source, but iseffectively applicable in a case where the heat source in the heatsource fluid heater 1 is a low-temperature heat source such as biomassfuel, solar energy, factory exhaust heat or hot spring heat. Further,the present embodiment is effectively applicable in any heat source in acase where a temperature of the heat source fluid in the inlet of theheat absorbing module 16 a is 200° C. or less. This is true oftwenty-fourth to thirty-second embodiments to be described later. Thereason is that in a case where the heat source in the heat source fluidheater 1 is a low-temperature heat source, COP of the refrigerator 16 islower, and the energy utilization rate in a case where the presentembodiment is not applied is low. According to the present embodiment,it is possible to remarkably improve the energy utilization rate in acase where the heat source in the heat source fluid heater 1 is thelow-temperature heat source. This is true of the twenty-fourth tothirty-second embodiments to be described later.

In addition, the configuration of the present embodiment is effectivelyapplicable in a case where the maximum temperature of the heat sourcefluid in the heat source fluid path 3 is 200° C. or less.

Twenty-fourth Embodiment

FIG. 26 is a schematic diagram showing the configuration of a coolingsystem according to a twenty-fourth embodiment.

The heater 31 in FIG. 26, as similar to the second embodiment, heats thewater by using the heat source fluid flowing upstream of the heatabsorbing module 16 a. In the present embodiment, a temperature of theheat source fluid in the inlet of the heater 31 is higher than atemperature of the heat source fluid in the inlet of the heat absorbingmodule 16 a. Therefore, the water tends to be easily heated to a highertemperature.

Twenty-fifth Embodiment

FIG. 27 is a schematic diagram showing the configuration of a coolingsystem according to a twenty-fifth embodiment.

The heat absorbing module 16 a and the heater 31 in FIG. 27 are, assimilar to the third embodiment, arranged in parallel to the flow of theheat source fluid. In the present embodiment, since a temperature of theheat source fluid in the inlet of the heater 31 is equal to atemperature of the heat source fluid in the inlet of the heat absorbingmodule 16 a, both of the heat absorbing module 16 a and the water tendto be easily heated to a high temperature as much as possible.

Twenty-sixth Embodiment

FIG. 28 is a schematic diagram showing the configuration of a coolingsystem according to a twenty-sixth embodiment.

The hot water tank 32 and the water path 34 in FIG. 28 are, as similarto the fourth embodiment, replaced by the heat use destination 37 andthe circulation water path 38. The water in the present embodiment isheated and discharged by the heat releasing module 16 c. The heater 31uses the heat source fluid to heat this water and produce water to beused as the hot water. The hot water is conveyed through the circulationwater path 38 to be supplied to the heat use destination 37. An exampleof the heat use destination 37 includes floor heating.

The floor heating is generally used in winter. Accordingly, in a casewhere the heat use destination 37 is the floor heating, there isestimated a high possibility that an application of the refrigerator 16is performed for cooling a device such as a server computer rather thanfor cooling a facility such as building cooling. This is because ingeneral, the former is used in summer and the latter is used regardlessof seasons.

Twenty-seventh Embodiment

FIG. 29 is a schematic diagram showing the configuration of a coolingsystem according to a twenty-seventh embodiment.

The heat source fluid path 3 in FIG. 29, as similar to the fifthembodiment, includes a first bypass flow path 44 bypassing a first flowpath provided with the heat absorbing module 16 a, and a second bypassflow path 48 bypassing a second flow path provided with the heater 31.

In the present embodiment, upon performing both of the cold heatproduction and the hot water production, the valves 41, 42, 45, 46 areopened and the valves 43, 47 are closed. In addition, upon performing anoperation of placing importance on only the cold heat production, thevalves 41, 42, 47 are opened and the valves 43, 45, 46 are closed. Inaddition, upon performing only the hot water production, the valves 43,45, 46 are opened and the valves 41, 42, 47 are closed.

As described above, according to the present embodiment, it is possibleto select three kinds of operations in regard to the cold heatproduction and the hot water production by using the first and secondbypass flow paths 44, 48.

Twenty-eighth Embodiment

FIG. 30 is a schematic diagram showing the configuration of a coolingsystem according to a twenty-eighth embodiment.

The cooling system in FIG. 30 includes the components shown in FIG. 27,and besides, the plurality of valves 51 to 54. This configuration is thesame as that of the sixth embodiment.

In the present embodiment, upon performing both of the cold heatproduction and the hot water production, the valves to 54 are opened. Inaddition, upon performing an operation of placing importance on only thecold heat production, the valves 51, 52 are opened and the valves 53, 54are closed. In addition, upon performing only the hot water production,the valves 53, 54 are opened and the valves 51, 52 are closed.

As described above, according to the present embodiment, it is possibleto select three kinds of operations in regard to the cold heatproduction and the hot water production by using the first and secondbranch flow paths 37, 38.

Twenty-ninth Embodiment

FIG. 31 is a schematic diagram showing the configuration of a coolingsystem according to a twenty-ninth embodiment.

The cooling system in FIG. 31 includes the heat source fluid heater 21,the heat source fluid pump 22 and the heat source fluid path 23 inaddition to the components shown in FIG. 25. This configuration is thesame as that of the seventh embodiment. In the explanation in FIG. 31,as similar to the explanation in FIG. 44, the first heat source fluidheater 1, the first heat source fluid pump 2, the first heat sourcefluid path 3, the second heat source fluid heater 21, the second heatsource fluid pump 22 and the second heat source fluid path 23 areadopted as titles. The heat source fluid in the first heat source fluidpath 3 is called the first heat source fluid, and the heat source fluidin the second heat source fluid path 23 is called the second heat sourcefluid.

The first heat source fluid is heated by the first heat source fluidheater 1, and is lowered in temperature by heating the second heatsource fluid in the second heat source fluid heater 21. The second heatsource fluid is heated by the second heat source fluid heater 21 to heatthe heat absorbing module 16 a, and is thereby lowered in temperature.

The refrigerator 16 includes the heat absorbing module 16 a, the coolingmodule 16 b and the heat releasing module 16 c, and the cooling mediumis contained in the refrigerator 16. The cooling module 16 b cools thecooled fluid by evaporation heat of the cooling medium. The heatabsorbing module 16 a heats the cooling medium by the second heat sourcefluid to be vaporized or desorbed. The heat releasing module 16 c coolsthe cooling medium or the adsorption agent by the cooling water to causethe cooling medium to be vaporized or desorbed.

The cooled fluid is cooled by the cooling module 16 b to cool the coldload 19, and is increased in temperature. The cooling water is increasedin temperature by cooling the heat releasing module 16 c, which issupplied to the heater 31.

In the present embodiment, the heater 31 is provided in the second heatsource fluid path 23. The heater 31 heats the water from the water path34 by using the second heat source fluid to produce the water to be usedas the hot water. The second heat source fluid discharged from the heatabsorbing module 16 a flows into the heater 31 to heat the water in theheater 31, and is thereby lowered in temperature.

Here, the cooling system in FIG. 25 and the cooling system in FIG. 31will be compared.

In FIG. 25, since separated substances are accumulated in therefrigerator 16 (heat absorbing module 16 a) or the heater 31 dependingupon components contained in the heat source fluid, it is necessary tofrequently disassemble the refrigerator 16 or the heater 31 for thecleaning, but the disassembly of the refrigerator 16 or the heater 31 isnot preferable. Further, it is also not preferable to disassemble thewater path 34 used in bathing facilities or for dish washing inrestaurants. On the other hand, in FIG. 31, since not the refrigerator16 or the heater 31 but the second heat source fluid heater 21 isdisassembled and cleaned, it is not necessary to disassemble therefrigerator 16, the heater 31 and the water path 34.

As described above, the cooling system according to the presentembodiment uses the second heat source fluid to heat the water of thefirst temperature and produce the water of the second temperature to beused as the hot water. Therefore, according to the present embodiment,it is possible to effectively use the exhaust heat in the coolingsystem.

Thirtieth Embodiment

FIG. 32 is a schematic diagram showing the configuration of a coolingsystem according to a thirtieth embodiment.

The heater 31 in FIG. 32, as similar to the eighth embodiment, isprovided in the first heat source fluid path 3, and heats the water byusing the first heat source fluid flowing downstream of the second heatsource fluid heater 21. In many cases a temperature of the first heatsource fluid in the inlet of the heater 31 in the present embodiment ishigher than a temperature of the second heat source fluid in the inletof the heater 31. In the twenty-ninth embodiment. Therefore, the watertends to be easily heated to a higher temperature.

Thirty-First Embodiment

FIG. 33 is a schematic diagram showing the configuration of a coolingsystem according to a thirty-first embodiment.

The heater 31 in FIG. 33, as similar to the ninth embodiment, heats thewater by using the first heat source fluid flowing upstream of thesecond heat source fluid heater 21. In the present embodiment, atemperature of the first heat source fluid in the inlet of the heater 31is higher than a temperature of the first heat source fluid in the inletof the second heat source fluid heater 21. Therefore, the water tends tobe easily heated to a higher temperature.

FIG. 34 is a schematic diagram showing the configuration of a coolingsystem according to a modification of the thirty-first embodiment.

The heater 31 in FIG. 34, as similar to the modification of the ninthembodiment, heats the water by using the second heat source fluidflowing upstream of the heat absorbing module 16 a. In the presentmodification, a temperature of the second heat source fluid in the inletof the heater 31 is higher than a temperature of the second heat sourcefluid in the inlet of the heat absorbing module 16 a. Therefore, thewater tends to be easily heated to a higher temperature.

Thirty-Second Embodiment

FIG. 35 is a schematic diagram showing the configuration of a coolingsystem according to a thirty-second embodiment.

The cooling system in FIG. 35, as similar to the tenth embodiment,includes the first and second heaters 31 a, 31 b instead of the heater31.

The first heat source fluid is heated by the first heat source fluidheater 1, and is lowered in temperature by heating the second heatsource fluid in the second heat source fluid heater 21. The second heatsource fluid is heated by the second heat source fluid heater 21 to heatthe heat absorbing module 16 a, and is thereby lowered in temperature.

The refrigerator 16 includes the heat absorbing module 16 a, the coolingmodule 16 b and the heat releasing module 16 c, and the cooling mediumis contained in the refrigerator 16. The cooling module 16 b cools thecooled fluid by evaporation heat of the cooling medium. The heatabsorbing module 16 a heats the cooling medium by the second heat sourcefluid to be vaporized or desorbed. The heat releasing module 16 c coolsthe cooling medium or the adsorption agent by the cooling water to causethe cooling medium to be liquidized or adsorbed.

The cooled fluid is cooled by the cooling module 16 b to cool the coldload 19, and is thereby increased in temperature. The cooling water isincreased in temperature by cooling the heat releasing module 16 c,which passes through the second heater 31 b and the first heater 31 a onthe water path 34 in that order, and is reserved in the hot water tank32 as the hot water.

FIG. 36 is a schematic diagram showing the configuration of a coolingsystem according to a modification of the thirty-second embodiment.

The first heater 31 a in FIG. 36, as similar to the modification of thetenth embodiment, heats the water by using the first heat source fluidflowing upstream of the second heat source fluid heater 21. Further, thesecond heater 31 b in FIG. 36, as similar to the modification of thetenth embodiment, heats the water by using the second heat source fluidflowing upstream of the heat absorbing module 16 a.

As described above, the cooling system in the present embodimentincludes the first and second heaters 31 a, 31 b instead of the heater31. In a case of adopting this configuration, the heat exchangers in thecooling system increase in number, but the cooling system can bedesigned such that a difference in temperature between the heating fluidand the heated fluid is made small. Specifically, the cooling system canbe designed such that a difference in temperature between the first heatsource fluid and the second heat source fluid is made small. As aresult, according to the present embodiment, the water tends to beeasily heated to a higher temperature.

While certain embodiments have been described, these embodiments havebeen presented by way of example only, and are not intended to limit thescope of the inventions. Indeed, the novel systems described herein maybe embodied in a variety of other forms; furthermore, various omissions,substitutions and changes in the form of the systems described hereinmay be made without departing from the spirit of the inventions. Theaccompanying claims and their equivalents are intended to cover suchforms or modifications as would fall within the scope and spirit of theinventions.

1. An exhaust heat collecting system of collecting exhaust heat in afluid treatment system comprising: a fluid path configured to include atleast an operating fluid path or a cooled fluid path among a first heatsource fluid path, a second heat source fluid path, the operating fluidpath and the cooled fluid path, the first heat source fluid pathconveying a first heat source fluid, the second heat source fluid pathconveying a second heat source fluid heated by heat of the first heatsource fluid, the operating fluid path conveying an operating fluid, thecooled fluid path conveying a cooled fluid, the operating fluid beingconveyed through or not through an evaporator that vaporizes theoperating fluid by using the first or second heat source fluid, thecooled fluid being conveyed through a cooling module that cools thecooled fluid; and a fluid treatment module configured to include anexpansion module that rotates and drives to expand the operating fluid,a power generator that is connected to a rotational shaft of theexpansion module, and a condenser that condenses the operating fluid, orconfigured to include a heat absorbing module that absorbs heat of thefirst or second heat source fluid, and a heat releasing module thatreleases heat received from the cooled fluid and heat absorbed by theheat absorbing module, the exhaust heat collecting system comprising: awater path configured to supply water to the condenser or the heatreleasing module, heat the water by the condensation in the condenser orby the heat release in the heat releasing module, and convey the waterof a first temperature discharged from the condenser or the heatreleasing module; and a heater configured to heat the water from thewater path by using the first heat source fluid, the second heat sourcefluid or the operating fluid to produce the water of a secondtemperature to be used as hot water or to produce steam.
 2. The exhaustheat collecting system of claim 1, wherein the heater heats the water byusing the first or second heat source fluid that exists downstream orupstream of the evaporator or the heat absorbing module.
 3. The exhaustheat collecting system of claim 1, wherein the first or second heatsource fluid path is branched into a first branch flow path providedwith the evaporator or the heat absorbing module, and a second branchflow path provided with the heater.
 4. The exhaust heat collectingsystem of claim 3, comprising at least one of a first valve provided inthe first branch flow path, and a second valve provided in the secondbranch flow path.
 5. The exhaust heat collecting system of claim 1,wherein the first or second heat source fluid path comprises at leastone of a first bypass flow path that bypasses a first flow path providedwith the evaporator or the heat absorbing module, and a second bypassflow path that bypasses a second flow path provided with the heater. 6.The exhaust heat collecting system of claim 1, wherein the fluidtreatment system further comprises a heat source fluid heater configuredto heat the second heat source fluid by the heat of the first heatsource fluid, the heater heating the water by using the first heatsource fluid that exists downstream or upstream of the heat source fluidheater.
 7. The exhaust heat collecting system of claim 1, comprising, asthe heater, a first heater configured to heat the water by the heat ofthe first heat source fluid, and a second heater that configured to heatthe water by the heat of the second heat source fluid.
 8. The exhaustheat collecting system of claim 7, wherein one of the first and secondheaters is heated by the other of the first and second heaters, andheats the water flowing out from the other of the first and secondheaters.
 9. The exhaust heat collecting system of claim 1, wherein theoperating fluid path is branched into a first fluid path provided withthe expansion module and the condenser, and a second fluid path providedwith the heater.
 10. The exhaust heat collecting system of claim 9,wherein the first and second fluid paths merge into a third fluid paththat is provided with the evaporator, and the third fluid path isbranched into the first and second fluid paths.
 11. The exhaust heatcollecting system of claim 1, wherein the operating fluid path comprisesa fourth fluid path that conveys the operating fluid discharged from anexhaust port of the expansion module and is provided with the condenser,and a fifth fluid path that conveys the operating fluid extracted froman extraction port of the expansion module and is provided with theheater.
 12. The exhaust heat collecting system of claim 11, wherein thefourth and fifth fluid paths merge into a sixth fluid path that isprovided with the evaporator, and the sixth fluid path conveys theoperating fluid to the expansion module.
 13. The exhaust heat collectingsystem of claim 9, comprising at least one of a valve provided in thefirst or fourth fluid path and a valve provided in the second or fifthfluid path.
 14. The exhaust heat collecting system of claim 9,comprising, as the heater, a third heater provided in the second orfifth fluid path, and a fourth heater provided downstream of the thirdheater in the second or fifth fluid path.
 15. The exhaust heatcollecting system of claim 14, wherein the water path is branched into afirst water path provided with the condenser and a second water pathprovided with the fourth heater, and the first and second water pathsmerge into a third water path that is provided with the third heater.16. The exhaust heat collecting system of claim 14, comprising at leastone of a valve provided in the first water path and a valve provided inthe second water path.
 17. The exhaust heat collecting system of claim1, wherein the heater heats the water by using the operating fluid thatexists upstream of the expansion module.
 18. The exhaust heat collectingsystem of claim 1, wherein the water path circulates the water betweenthe heater and the condenser or the heat releasing module.
 19. Theexhaust heat collecting system of claim 1, wherein a maximum temperatureof the first heat source fluid, the second heat source fluid or theoperating fluid is equal to or less than 200° C.
 20. The exhaust heatcollecting system of claim 1, wherein the first heat source fluid is hotspring water or a fluid that is heated in a heat source fluid heaterthat obtains heat from a heat source of non-fossil fuel.